Periodic blow-out air lubrication system and rotary valve for periodic blow-out air lubrication system

Abstract

A periodic blow-out air lubrication system is provided with: a plurality of air blow-out ports (10) provided in the bottom of a ship; an air supply unit (20) that supplies air to the plurality of air outlets (10) via the duct path (50); a rotary path switching means (30) provided midway along the duct path (50); and a control unit (40) that controls the rotation-type path switching unit (30). The downstream side of the rotary path switching unit (30) is provided with a plurality of branch ducts (52) as duct paths (50) leading to the plurality of air outlets (10), the air outlets (10) to which air is supplied are switched in a predetermined order by the rotation of the valve body of the rotary path switching unit (30), and the air outlets (10) to which air is supplied are switched in a predetermined order by the rotation of the valve body of the rotary path switching unit (30). Air can be periodically blown out from all of the plurality of air outlets (10). Provided is a periodic blow-out air lubrication system which can be installed in a limited in-ship space, periodically blow out air to the bottom of a ship, thereby exhibiting a frictional resistance reduction effect by air lubrication, and which is also excellent in durability and maintainability.

Description

TECHNICAL FIELD

[0001] The present application relates to an air-blowing lubrication system that blows air to the bottom of a ship to reduce the frictional resistance of the ship body, and a rotary valve used for the periodic air-blowing lubrication system. BACKGROUND

[0002] As a ship body frictional resistance reduction device, an air lubrication system that blows air to the bottom of a ship to reduce the frictional resistance of the ship body is known, and as a method of improving the frictional resistance reduction rate of the air lubrication system, there are a continuous blowing method and a periodic blowing method.

[0003] Here, Patent Document 1 discloses a fluid monitoring device that includes a sensor portion including a plurality of ultrasonic probes of a piezoelectric type fixed in a manner that an ultrasonic wave transmission / reception surface is inclined with respect to a surface along a bottom portion, and a signal processing portion that processes a signal detected by the ultrasonic probe, the fluid monitoring device being installed to the bottom portion of a ship to monitor a fluid around the bottom portion, and in claim 4, a ship body frictional resistance reduction system is described that includes the fluid monitoring device and a bubble spouting mechanism that spouts bubbles to the bottom portion, and the signal processing portion controls a bubble spouting timing in the bubble spouting mechanism based on a probability distribution and a flow velocity distribution. Further, in claim 5, the signal processing portion of the ship body frictional resistance reduction system is described that controls the bubble spouting timing of the bubble spouting mechanism in a prescribed period and in a manner that becomes a prescribed duration.

[0004] In addition, Patent Document 2 discloses an unmanned groundwater pumping distribution opening and closing device that provides a water inlet on one side of an inflow chamber, provides a fixed plate on the other side and annularly forms a plurality of water passage holes, installs a spring to the fixed plate, provides a rotating shaft of a rotating opening and closing plate that can abut to the rotating shaft, annularly provides a plurality of opening and closing holes that can coincide with the water passage holes on the rotating opening and closing plate, forms the opening and closing holes to be freely opened and closed in a state of being individually or freely combined by an opening and closing valve, forms a worm gear on an outer peripheral portion, forms a configuration that can rotate at a reduced speed or can stop for a certain time by a motor connected to a worm shaft extension, provides a position sensor that senses a rotation angle on an outer side portion of the rotating shaft, and can control water supply from each delivery pipe by operating a pumping pump and the motor by a configuration circuit portion of a control circuit portion.

[0005] In addition, Patent Document 3 discloses a rotary valve that selectively communicates or cuts off a plurality of outflow paths to switch the flow path by relative movement of a housing and a valve body, in which a through hole is provided near the outflow path of the housing, and a first communication path that communicates a part of the outflow path to form a flow path, and a second communication path that, when a part of the outflow path is communicated through the first communication path, communicates the other outflow path that is cut off with the through hole, and causes the fluid in the outflow path to be discharged from the through hole, are provided to the valve body.

[0006] In addition, Patent Document 4 discloses a flow path switching valve including: a drive section having a motor; a base fixed to the drive section and provided with a plurality of flow path tubes on a same circumference centered on a drive shaft of the drive section; a circular plate having at least one window on a circumference corresponding to the flow path tubes of the base; a power transmission unit engaged to the drive shaft in a detachable manner, transmitting rotation from the drive shaft to the circular plate and pressing the circular plate against the flow path tubes provided on the base; and a cover body installed to the base in an openable and closable manner, having a cavity in which the circular plate and the power transmission unit are accommodated and sealed, and at least one flow path tube communicating with the cavity.

[0007] Prior Art Documents Patent Documents Patent Document 1: Japanese Patent Application Publication No. 2011-163774 Patent Document 2: Japanese Patent Application Publication No. H9-280393 Patent Document 3: Japanese Patent Application Publication No. 2004-232698 Patent Document 4: Japanese Patent Application Publication No. S55-8403 (Japanese Patent Application Publication No. S56-111367) SUMMARY PROBLEMS TO BE SOLVED BY THE INVENTION In actual ships, because of limited space, it is difficult to provide a plurality of blowout devices when an air lubrication system is applied.

[0008] Patent Document 1 describes controlling the blowout timing of bubbles in a prescribed cycle and in a manner that becomes a continuous time, but uses a solenoid valve when opening and closing a bubble introduction path from a bubble generating blower to a bubble blowout port, raising concerns about electronic control failure and durability.

[0009] Patent Document 2 relates to an opening and closing valve for pumping water, and is not an air lubrication system for reducing the frictional resistance of a ship body. In addition, it is necessary to provide an equal number of opening and closing holes in a rotating opening and closing plate to the plurality of water passage holes formed in a fixed plate, and it is also necessary to provide a plurality of opening and closing valves combined with the opening and closing holes, and the like, and the structure is complex.

[0010] Patent Documents 3 and 4 also relate to rotary valves, but are not air lubrication systems for reducing the frictional resistance of a ship body. In addition, although it is a device that makes fluid flow or blocked by opening and closing a fluid outlet provided to a fixed plate or a cover body by rotation of a valve seat or a circular plate, it is different from the technical idea of periodically supplying air.

[0011] Therefore, an object of the present application is to provide a periodic air blow lubrication system and a rotary valve for a periodic air blow lubrication system, which can be installed in a limited ship interior space, periodically blows air to a ship bottom to exert an air lubrication-based friction resistance reduction effect, and is excellent in durability and maintainability.

[0012] Means for solving the above-described technical problem The periodic air blow lubrication system according to the above-described means 1 is an air lubrication system that periodically blows air to a ship bottom of a ship to reduce friction resistance of a ship body, and includes: a plurality of air blow outlets provided to the ship bottom; an air supply unit that supplies air to the plurality of air blow outlets via a pipe path; a rotary path switching unit provided midway in the pipe path; and a control unit that controls the rotary path switching unit, has a plurality of branch pipes as the pipe path to the plurality of air blow outlets on a downstream side of the rotary path switching unit, and switches the air blow outlets to which air is supplied in a prescribed order by rotation of a valve body of the rotary path switching unit, and can periodically blow air from all of the plurality of air blow outlets by rotation of the valve body of the rotary path switching unit.

[0013] According to the present application according to the above-described means 1, air supplied from the air supply unit can be distributed to each of the air blow outlets by the rotary path switching unit and blown from the ship bottom, and thus, compared to a case where a plurality of air supply units or switching units are provided, the required installation space can be reduced. In addition, since the control unit is configured to cause air to be periodically and intermittently blown from all of the air blow outlets by controlling rotation of the valve body of the rotary path switching unit, compared to a structure in which a plurality of solenoid valves are used to frequently open and close, the number of constituent components and electronic control devices can be reduced, and durability and maintainability can be improved.

[0014] The present application according to the above-described means 2 is characterized in that the rotary path switching unit is configured to communicate with a certain one of the branch pipes regardless of the rotation angle of the valve body.

[0015] According to the present application according to the above-described means 2, the rotary path switching unit always communicates with the branch pipe that is a pressure release passage, and thus, excessive increase in internal pressure of the rotary path switching unit is prevented, and increase in rotation torque and increase in air leakage, and the like, can be suppressed. In addition, since the pipe path does not become a closed state in the periodic blowing of air, the operation of the air supply unit is stable.

[0016] The present application according to the above-described means 3 is characterized in that the rotary path switching unit is configured to be able to adjust a duty ratio that is a ratio of time during which air is blown from the air blow outlet to time during which blowing is stopped, and the control unit performs mode setting according to a blowing mode of air, and controls the duty ratio by the rotation of the valve body.

[0017] According to the present application described in the item 3, by the control unit changing the duty ratio set in the rotating type path switching unit according to the mode, the blowing interval can be changed according to the sailing condition of the ship, and the frictional resistance reduction based on air lubrication can be effectively performed.

[0018] The present application described in the item 4 is characterized in that the control unit changes the rotation speed of the valve body of the rotating type path switching unit according to the mode setting of the blowing mode of the air.

[0019] According to the present application described in the item 4, the blowing period can be changed by changing the rotation speed, and the air can be blown at a period corresponding to each mode.

[0020] The present application described in the item 5 is characterized in that the rotating type path switching unit has a structure capable of communicating all the plurality of branch pipes, and the control unit performs the control of adjusting the rotation angle of the valve body of the rotating type path switching unit to continuously blow the air from all the air blow outlets according to the mode setting of the blowing mode of the air.

[0021] According to the present application described in the item 5, by the selection of the mode, one rotating type path switching unit can switch between the periodic blowing and the continuous blowing.

[0022] The present application described in the item 6 is characterized in that the rotating type path switching unit has a structure capable of blocking all the plurality of branch pipes, and the control unit performs the control of adjusting the rotation angle of the valve body of the rotating type path switching unit to block all the branch pipes when the operation of the air supply unit is stopped.

[0023] According to the present application described in the item 6, when the blowing is not performed, the rotation angle of the valve body of the rotating type path switching unit can be controlled to block the branch pipes, so that, for example, water does not flow backward from the air blow outlets to all the branch pipes.

[0024] The present application described in the item 7 is characterized in that the rotating type path switching unit has a structure capable of selecting a prescribed branch pipe from among the plurality of branch pipes, and the control unit performs the control of periodically supplying the air from the prescribed air blow outlet by rotating or reversing the valve body according to the mode setting of the blowing mode of the air.

[0025] According to the present application described in the item 7, for example, in a mode in which the air blow outlets located at the ship sides are used for periodic blowing in the case where the ship body is subjected to a large roll in which the air blow outlets located at the ship sides are exposed to the water, or a mode in which the air blow outlets located at the left and right of the ship body are alternately switched and all the air blow outlets are used for periodic blowing in the case where the ship body is subjected to a moderate roll, the valve body is rotated or rotated in the reverse direction so that air is distributed to the selected prescribed branch pipes, and thus periodic blowing corresponding to each mode is performed.

[0026] The present application described in the item 8 is characterized in that the rotating type path switching unit has a structure in which a prescribed branch pipe among a plurality of branch pipes can be selected, and the control unit performs mode setting according to the blowing mode of the air, and controls the supply of air from the prescribed air blow outlet by stopping the rotation of the valve body.

[0027] According to the present application described in the item 8, for example, in a mode in which the air blow outlets located at the center of the ship body are used for continuous blowing in the case where the ship body is subjected to a roll in which the air blow outlets located at the ship sides are exposed to the water, or the like, by fixing the rotation angle of the valve body so that air is distributed to only the selected prescribed branch pipe, continuous blowing corresponding to the mode can be performed.

[0028] The present application described in the item 9 is characterized in that, by adopting at least one of a cooling unit and a temperature rise countermeasure configuration, a countermeasure against temperature rise of the rotating type path switching unit caused by the supply of air warmed up from the air supply unit is taken.

[0029] According to the present application described in the item 9, it is possible to prevent performance degradation such as an increase in leakage of the rotating type path switching unit caused by temperature rise.

[0030] The rotating valve for a periodic blowing air lubrication system according to the item 10 is a rotating valve for a rotating type path switching unit of a periodic blowing air lubrication system, and is characterized by including: a housing having an inlet for air and a plurality of outlets; a rotating disc serving as a valve body, which is housed in the housing and has a single rotating disc aperture; a fixed disc serving as a valve seat, which allows the rotating disc to slide and has a plurality of fixed disc apertures that guide air to the plurality of outlets; a biasing unit that presses the rotating disc toward the fixed disc; and a driving unit that rotates the rotating disc via a shaft.

[0031] According to the present application described in the item 10, by rotating the rotating disc, the rotating disc aperture overlaps the fixed disc aperture in a prescribed order, and air flows out to the branch pipes and is blown out from the air blow outlets through the fixed disc apertures in which the rotating disc aperture overlaps, and thus it is possible to periodically supply air from the plurality of outlets with a simple structure.

[0032] The present application according to the scheme 11 is characterized in that the single rotating disc hole is configured in a shape that overlaps at least one of the plurality of fixed disc holes regardless of the rotation angle.

[0033] According to the present application according to the scheme 11, since the rotating disc hole is always overlapped with one of the fixed disc holes, the rotating valve is always in communication with the branch pipe as a pressure release passage, so that the internal pressure of the rotating valve is prevented from excessively rising, and the increase of the rotating torque and the increase of the air leakage are suppressed.

[0034] The present application according to the scheme 12 is characterized in that the rotating valve is configured to be capable of exchanging the other rotating disc as a valve body having another rotating disc hole having a different shape from the rotating disc hole of the rotating disc, so that the duty ratio is variable.

[0035] According to the present application according to the scheme 12, the duty ratio can be changed by replacing the rotating disc with another rotating disc having a different shape of the rotating disc hole.

[0036] The present application according to the scheme 13 is characterized in that an adjustment disc for adjusting the duty ratio is further provided, and is configured to be capable of changing the overlapping hole formed by the overlapping of the rotating disc hole and the adjustment disc hole of the adjustment disc, or the overlapping of the adjustment disc hole and the fixed disc hole, so that the duty ratio is variable.

[0037] According to the present application according to the scheme 13, the size of the overlapping hole formed by the overlapping of the rotating disc hole and the adjustment disc hole, or the adjustment disc hole and the fixed disc hole can be changed by changing the position of the adjustment disc, so that the duty ratio is changed.

[0038] The present application according to the scheme 14 is characterized in that the driving speed of the driving unit that rotates the rotating disc is variable.

[0039] According to the present application according to the scheme 14, the blowing period can be changed by changing the rotation speed of the rotating disc.

[0040] The present application according to the scheme 15 is characterized in that the rotating disc hole has a rotation angle that overlaps all of the plurality of fixed disc holes by the rotation of the rotating disc, and the plurality of fixed disc holes that communicate to guide the air to the plurality of outlets are configured to be capable of continuously blowing the air by the adjustment of the rotation angle of the rotating disc.

[0041] According to the present application according to the scheme 15, the one rotating valve can be switched between the periodic blowing and the continuous blowing.

[0042] The application according to the scheme 16 is characterized in that the rotating circular plate opening is configured to have a rotation angle that does not overlap any of the plurality of fixed circular plate openings by rotation of the rotating circular plate, and by adjusting the rotation angle of the rotating circular plate, the plurality of fixed circular plate openings that guide air to the plurality of outlets can be blocked to stop the blowing of air.

[0043] According to the application according to the scheme 16, when not blowing, by adjusting the rotation angle of the rotating circular plate so that all the fixed circular plate openings are blocked by the rotating circular plate, the outlet can be blocked to block the branch pipe.

[0044] The application according to the scheme 17 is characterized in that at least one of a passage for cooling water that cools the rotating valve in the housing, and a rotating circular plate that has a degree of freedom in the axial direction with respect to the shaft to apply force to the rotating circular plate toward the fixed circular plate.

[0045] According to the application according to the scheme 17, when the rotating valve is cooled by cooling water, the temperature rise can be suppressed, or when the temperature rise is suppressed by applying force to the rotating circular plate toward the fixed circular plate, the gap between the rotating circular plate and the fixed circular plate is enlarged, thereby preventing performance degradation such as an increase in leakage of the rotating valve due to the supply of high-temperature air from the air supply unit.

[0046] The application according to the scheme 18 is characterized in that, in order to prevent eccentricity of the shaft that accompanies rotation caused by offset of the rotating circular plate opening, any of the following countermeasures is taken: a countermeasure of providing an anti-eccentric opening of the same shape at a symmetrical position of the rotating circular plate opening of the rotating circular plate, a countermeasure of performing an anti-eccentric counterbore process of an approximate shape at a symmetrical position of the rotating circular plate opening, or a countermeasure of providing a counterweight in the vicinity of the rotating circular plate opening.

[0047] According to the application according to the scheme 18, by any of the anti-eccentric opening, the anti-eccentric counterbore process, or the counterweight, eccentricity of the shaft when the rotating circular plate rotates can be prevented.

[0048] The application according to the scheme 19 is characterized in that the internal space of the rotating circular plate of the housing on the upstream side has a prescribed volume, and equalization of air that enters from the inlet is achieved.

[0049] According to the application according to the scheme 19, by the internal space having a prescribed volume, pressure fluctuations of the rotating valve and the pipe path can be suppressed.

[0050] Inventive Effects The periodic air blowing lubrication system according to the present application can reduce the required installation space compared to the case where a plurality of air supply units or switching units are provided, by distributing the air supplied from the air supply unit to each air blowing outlet using the branch pipe and blowing the air from the ship bottom by the rotation type path switching unit. In addition, since the control unit controls the rotation of the valve body of the rotation type path switching unit to periodically and intermittently blow the air from all the air blowing outlets to the ship bottom, the durability and maintainability can be improved by reducing the components and electronic control devices compared to the structure where a plurality of solenoid valves are frequently opened and closed.

[0051] In addition, in the case where the rotation type path switching unit is configured to communicate with a certain branch pipe regardless of the rotation angle of the valve body, the rotation type path switching unit always communicates with the branch pipe as a pressure release passage, so that the internal pressure of the rotation type path switching unit is prevented from excessively rising, and the increase in the rotation torque and the increase in air leakage are suppressed. In addition, since the pipe path does not become a closed state during the periodic blowing of the air, the operation of the air supply unit is stable.

[0052] In addition, in the case where the rotation type path switching unit is configured to be able to adjust the duty ratio as the time ratio of blowing the air from the air blowing outlet and stopping the blowing, the control unit performs mode setting according to the blowing mode of the air, and controls the duty ratio by the rotation of the valve body, the control of the duty ratio set in the rotation type path switching unit according to the mode change by the control unit is performed, so that the blowing interval can be changed according to the sailing condition of the ship, and the frictional resistance reduction based on the air lubrication can be effectively performed.

[0053] In addition, in the case where the control unit performs control to change the rotation speed of the valve body of the rotation type path switching unit according to the mode setting according to the blowing mode of the air, the blowing period can be changed by changing the rotation speed to blow the air at a period corresponding to each mode.

[0054] In addition, in the case where the rotation type path switching unit has a structure capable of communicating all the plurality of branch pipes, the control unit performs control to adjust the rotation angle of the valve body of the rotation type path switching unit to continuously blow the air from all the air blowing outlets according to the mode setting according to the blowing mode of the air, the periodic blowing and the continuous blowing can be switched by one rotation type path switching unit by the selection of the mode.

[0055] Further, in the case where the rotary path switching unit has a structure capable of blocking all of the plurality of branch pipes, in the case where the control unit controls the rotary angle of the valve body of the rotary path switching unit to block all of the branch pipes when the operation of the air supply unit is stopped, the rotary angle of the valve body of the rotary path switching unit can be controlled to block the branch pipes at the time of non-blowout, so that, for example, water does not flow backward from the air blowout port to all of the branch pipes.

[0056] Further, in the case where the rotary path switching unit has a structure capable of selecting a prescribed branch pipe among the plurality of branch pipes, in the case where the control unit performs mode setting according to the blowout mode of the air, and controls the air to be periodically supplied from the prescribed air blowout port by rotating or reversing the valve body, among modes such as a mode in which the air is periodically blown out using the air blowout port located near the center of the ship body in the case where the ship body undergoes a large roll to the extent that the air blowout port located near the ship side is exposed to water, or a mode in which the air blowout ports located on the left and right of the center of the ship body are alternately switched and the air is periodically blown out using all of the air blowout ports in the case where a moderate roll is generated, the valve body can be rotated or reversed so that the air is distributed to the selected prescribed branch pipe, and thus the periodic blowout corresponding to each mode can be performed.

[0057] Further, in the case where the rotary path switching unit has a structure capable of selecting a prescribed branch pipe among the plurality of branch pipes, in the case where the control unit performs mode setting according to the blowout mode of the air, and controls the air to be supplied from the prescribed air blowout port by stopping the rotation of the valve body, among modes such as a mode in which the air is continuously blown out using the air blowout port located near the center of the ship body in the case where the ship body undergoes a roll to the extent that the air blowout port located near the ship side is exposed to water, the rotation angle of the valve body can be fixed so that the air is distributed only to the selected prescribed branch pipe, and thus the continuous blowout corresponding to the mode can be performed.

[0058] Further, in the case where at least one of the cooling unit and the temperature rise countermeasure structure is employed, and a countermeasure against the temperature rise of the rotary path switching unit accompanying the supply of the warmed air from the air supply unit is taken, the performance reduction such as an increase in leakage of the rotary path switching unit due to the temperature rise can be prevented.

[0059] Further, the rotary valve for a periodic blowout air lubrication system according to the present application can periodically supply air from a plurality of outlets with a simple structure by rotating the rotary circular plate, the rotary circular plate apertures overlapping the fixed circular plate apertures in a prescribed order, and the air flowing out to the branch pipes and being blown out from the air blowout port through the fixed circular plate apertures in which the rotary circular plate apertures overlap.

[0060] Further, in a case where the single rotating disc hole is configured in a shape that overlaps at least one of the plurality of fixed disc holes regardless of the rotation angle, since the rotating disc hole necessarily overlaps a certain one of the fixed disc holes, the rotating valve is always in a state of communicating with the branch pipe that is a release passage of pressure, and thus excessive increase in internal pressure of the rotating valve is prevented, and increase in rotating torque and increase in air leakage, and the like, can be suppressed.

[0061] Further, in a case where the rotating valve is configured to be capable of exchanging the rotating disc having another rotating disc hole having a different shape from that of the rotating disc hole with another rotating disc as a valve body, and the duty ratio is variable, the duty ratio can be changed by replacing the rotating disc with another rotating disc having a different shape of the rotating disc hole.

[0062] Further, in a case where an adjustment disc for adjusting the duty ratio is further provided, and configured to be capable of changing the overlapping hole formed by overlapping of the rotating disc hole and the adjustment disc hole of the adjustment disc, or overlapping of the adjustment disc hole and the fixed disc hole, and the duty ratio is variable, the duty ratio can be changed by changing the position of the adjustment disc to change the size of the overlapping hole formed by overlapping of the rotating disc hole and the adjustment disc hole, or overlapping of the adjustment disc hole and the fixed disc hole.

[0063] Further, in a case where the driving unit that rotates the rotating disc is configured to be capable of changing the driving speed, the blowing period can be changed by changing the rotation speed of the rotating disc.

[0064] Further, in a case where the rotating disc hole has a rotation angle that overlaps all of the plurality of fixed disc holes by rotation of the rotating disc, and the plurality of fixed disc holes that communicate to guide air to the plurality of outlets are configured to be capable of continuously blowing air by adjustment of the rotation angle of the rotating disc, the one rotating valve can switch between periodic blowing and continuous blowing.

[0065] Further, in a case where the rotating disc hole has a rotation angle that does not overlap any of the plurality of fixed disc holes by rotation of the rotating disc, and the plurality of fixed disc holes that guide air to the plurality of outlets are blocked by adjustment of the rotation angle of the rotating disc to stop blowing of air, when blowing is not performed, the outlets can be blocked to block the branch pipe by adjusting the rotation angle of the rotating disc so that all of the fixed disc holes are blocked by the rotating disc.

[0066] Further, in a case where at least one of a passage of cooling water in which a cooling rotary valve is provided in the housing, and a configuration in which the rotary circular plate is given a degree of freedom in the axial direction with respect to the shaft to apply a force to the rotary circular plate toward the fixed circular plate, temperature rise can be suppressed by cooling the rotary valve with cooling water, or the gap between the rotary circular plate and the fixed circular plate can be prevented from widening when temperature rise is suppressed by applying a force to the rotary circular plate toward the fixed circular plate, thereby preventing performance degradation such as an increase in leakage of the rotary valve due to supply of high-temperature air from the air supply unit.

[0067] Further, in a case where any one of a countermeasure of providing an anti-eccentricity hole of the same shape at a position symmetrical to the rotary circular plate hole of the rotary circular plate, a countermeasure of performing anti-eccentricity counterboring processing of an approximate shape at a position symmetrical to the rotary circular plate hole, or a countermeasure of providing a counterweight in the vicinity of the rotary circular plate hole is taken in order to prevent eccentricity of the shaft accompanying rotation due to bias of the rotary circular plate hole, eccentricity of the shaft when the rotary circular plate rotates can be prevented by any one of the anti-eccentricity hole, the anti-eccentricity counterboring processing, or the counterweight.

[0068] Further, in a case where an internal space on the upstream side of the rotary circular plate configured as the housing has a prescribed volume, and uniformization of air entering from the inlet is achieved, pressure variation of the rotary valve and the piping path can be suppressed by the internal space having the prescribed volume. BRIEF DESCRIPTION OF DRAWINGS

[0069]

【 Figure 1 FIG. 1 is a schematic diagram of a cycle blow air lubrication system according to an embodiment of the present application.

[0070]

【 Figure 2 FIG. 2 is a schematic diagram of a rotary valve for the cycle blow air lubrication system.

[0071]

【 Figure 3 FIG. 3 is a diagram of a configuration example in which the cooling unit and the temperature rise countermeasure configuration are provided.

[0072]

【 Figure 4 FIG. 4 is a diagram showing overlap of the rotary circular plate hole and the fixed circular plate hole.

[0073]

【 Figure 5 FIG. 5 is a diagram regarding the shape of the rotary circular plate hole.

[0074]

【 Figure 6 FIG. 6 is a diagram showing a configuration example in which the duty ratio can be adjusted.

[0075]

【 Figure 7 FIG. 7 is a diagram showing a configuration example in which the duty ratio can be automatically adjusted.

[0076]

【 Figure 8 FIG. 8 is a diagram showing another example of the rotary circular plate.

[0077]

Figure 9

[0078]

Figure 10

[0079]

Figure 11

[0080]

Figure 12

[0081]

Figure 13

[0082] A periodic blowing air lubrication system and a rotating valve for a periodic blowing air lubrication system that explain an embodiment of the present application.

[0083] Figure 1 is a schematic view of the periodic blowing air lubrication system in the present embodiment.

[0084] The periodic blowing air lubrication system equipped in the ship 1 periodically blows air to the bottom of the ship 1 to reduce the frictional resistance of the hull, and has: a plurality of air blowing outlets 10 provided to the bottom; an air supply unit 20, which is an air blower or the like, that supplies air to the plurality of air blowing outlets 10 via a pipe path 50; a rotating type path switching unit 30 provided midway of the pipe path 50; and a control unit 40 that controls the rotating type path switching unit 30. In addition, a single main pipe 51 is provided as the pipe path 50 that connects the air supply unit 20 and the rotating type path switching unit 30, and a plurality of branch pipes 52 are provided as the pipe path 50 that leads to the plurality of air blowing outlets 10 on the downstream side of the rotating type path switching unit 30. Further, the rear side of the ship 1 is omitted in Figure 1

[0085] In addition, the air supply unit 20 can be an air blower, a bypass take-out unit from a supercharger of an engine, or a combination of the bypass take-out unit from the supercharger and the air blower, or the like.

[0086] The branch pipes 52 are provided one-to-one with the air blowing outlets 10, and one end is connected to the rotating type path switching unit 30 and the other end is connected to the air blowing outlets 10. The air sent out from the air supply unit 20 to the main pipe 51 is distributed to the prescribed branch pipes 52 by the rotating type path switching unit 30 and blown out from each air blowing outlet 10. ​

[0087] The rotation-type path switching unit 30 is provided between the main pipe 51 and the branch pipes 52, and has an air flow inlet to which the main pipe 51 is connected, and a plurality of air flow outlets to which the branch pipes 52 are connected one by one.

[0088] The control unit 40 switches the air flow outlets set to open and the air flow outlets set to closed in a prescribed order by controlling the rotation of the rotating member (valve body) in the rotation-type path switching unit 30. Thereby, the air blow outlets 10 to which air is supplied are switched in a prescribed order, and air is periodically blown out from the air blow outlets 10 toward the bottom of the ship. Further, in Figure 1 In the drawing, in addition to the image of the bubble flow generated in the case of the periodic blowing, the image of the bubble flow generated in the case of the continuous blowing described later is also shown.

[0089] By performing the periodic blowing, even if the amount of air blown out is the same, a larger frictional resistance reduction effect than in the case of the continuous blowing can be obtained. In addition, since the air supplied from the air supply unit 20 is distributed to each air blow outlet 10 via the branch pipes 52 by the rotation-type path switching unit 30 and blown out from the bottom of the ship, the required installation space can be reduced compared to the case where a plurality of air supply units 20 or switching units are provided.

[0090] In addition, the periodic blowing can also be performed using a structure in which a solenoid valve is used in the flow control of air, but in this structure, electronic control failure and durability are a concern. In contrast to this, the periodic blowing air lubrication system of the present embodiment is configured so that air is periodically and intermittently blown out from all the air blow outlets 10 toward the bottom of the ship by the control unit 40 controlling the rotation of the valve body of the rotation-type path switching unit 30, and therefore the electronic control device can be configured only as a motor or the like driving unit that rotates the valve body of the rotation-type path switching unit 30, and compared to a structure in which a plurality of solenoid valves are used to frequently open and close, the number of constituent parts and the electronic control device can be reduced, and durability and maintainability can be improved.

[0091] Figure 2 is a schematic view of a rotation valve for a periodic blowing air lubrication system, Figure 2 (a) of the same shows the overall structure, Figure 2 (b) of the same shows a rotating circular plate, Figure 2 (c) of the same is Figure 2 is an A-A cross-sectional view of (a) of the same, and shows a fixed circular plate.

[0092] In the present embodiment, a rotary valve is used as the rotary-type path switching unit 30. This periodic air blow-out air lubrication system rotary valve 30 is provided with: a housing 31 having an air inlet 31A and a plurality of air outlets 31B; a rotary disc 32 as a rotary member (valve body) housed in the housing 31 on the outlet 31B side and having a single rotary disc aperture 32A between the center portion and the outer edge portion; a fixed disc 33 as a valve seat for the rotary disc 32 to slide against and having a plurality of fixed disc apertures 33A between the center portion and the outer edge portion for guiding air to the plurality of outlets 31B; a biasing unit 34 for pressing the rotary disc 32 against the fixed disc 33; and a drive unit 36 for rotating the rotary disc 32 via a shaft 35A. In the center portion of the rotary disc 32 and the center portion of the fixed disc 33, a rotary disc shaft hole 32B and a fixed disc shaft hole 33B are formed, respectively, for the shaft (driven shaft) 35A to pass through.

[0093] The shaft 35A on the rotary disc side is connected to the drive shaft 35B of the drive unit 36 via a coupling 38, and the connection portion is covered by a shaft cover 37. As the coupling 38, a slotted coupling (eccentric coupling) having a circumferential slit applied to the outer circumferential surface is used, thereby eliminating the eccentricity of the shaft 35A and the drive shaft 35B. In order to improve the rotation stability, the shaft 35A is supported at two points by bearings 39 provided on the rotary disc 32 side and the coupling 38 side, respectively.

[0094] By rotating the rotary disc 32, the rotary disc aperture 32A overlaps the fixed disc aperture 33A in a prescribed order, and air flows out to the branch pipe 52 through the fixed disc aperture 33A in which the rotary disc aperture 32A overlaps, and is blown out from the air blow-out outlet 10, whereby air can be periodically supplied from the plurality of outlets 31B in a simple structure.

[0095] The gap between the rotating disc 32 and the fixed disc 33 is about 0.2 mm. The temperature of the compressed air supplied from the air supply unit 20, although depending on the pressure, is assumed to be about 100°C in an inland ship with a draft of about 5 m, and to exceed 200°C in an ocean-going large ship with a draft of about 20 m. When the portion of the shaft 35A that is located in the gap between the rotating disc 32 and the fixed disc 33 and that rotates to drive the rotating disc 32 elongates due to a temperature change, the size of the gap changes. Although also depending on the size of the elongated portion, the gap can change by about 0.1 mm when the temperature changes by 100°C. Therefore, by providing the rotating disc with a degree of freedom in the axial direction with respect to the shaft 35A, and by providing the fitting structure of the shaft 35A and the rotating disc 32, for example, as a key fitting, thereby providing a fitting structure that is free to move forward and backward but is not rotatable, and by using the urging unit 34 such as a spring to apply a force to the rotating disc 32 in the direction of the fixed disc 33, the enlargement of the gap when the shaft 35A elongates due to a temperature change is suppressed. With this temperature rise countermeasure configuration, it is possible to manage so that the size of the gap is within a prescribed range, and so that the performance of the rotary valve 30 is as designed. In addition, by applying a force using the urging unit 34, it is possible to manage so that the gap is within a prescribed range not only when the temperature changes, but also when there is wear over time and the like. In addition, it is also possible to use ceramic or the like, which has a small coefficient of thermal expansion, for the shaft 35A and the rotating disc 32 and the fixed disc 33, or to use a combination of materials and structures.

[0096] Further, as the shape of the rotating disc 32 and the fixed disc 33, any shape other than a circle that can function can be used, and the fixed disc 33 can also be configured to function as the housing 31. In addition, in the present embodiment, a so-called flat plate type rotary valve configured of a rotating disc 32 (valve body) and a fixed disc 33 is used as the rotary type path switching unit 30, but in addition thereto, a valve such as a cylinder type or a ball valve type can also be used as the rotary type path switching unit 30.

[0097] In addition, as another countermeasure to the problem of the enlargement of the gap between the rotating disc 32 and the fixed disc 33 due to the inflow of high-temperature air, it is possible to cite suppressing the elongation of the shaft 35A by providing a cooling unit to suppress a temperature rise.

[0098] Figure 3 is a drawing showing a configuration example in which a cooling unit and a temperature rise countermeasure configuration are provided, Figure 3 (a) of is a first configuration example, Figure 3 (b) of is a second configuration example.

[0099] In Figure 3In the first configuration example shown in (a), a first water-cooled heat exchanger 90A is provided as a cooling unit on the main pipe 51 upstream of the rotary valve 30. A cooling water circulation pipe 91 for supplying clean water (cooling water) as cooling water is provided through the first water-cooled heat exchanger 90A. Air supplied from the air supply unit 20 is cooled when passing through the first water-cooled heat exchanger 90A before entering the rotary valve 30. As a result, the temperature rise of the rotary valve 30 caused by air inflow can be suppressed.

[0100] The portion of the cooling water circulation pipe 91 extending outward from the first water-cooled heat exchanger 90A passes through the second water-cooled heat exchanger 90B. The second water-cooled heat exchanger 90B is equipped with a cooling seawater pipe 92 for the flow of cooling seawater (cooling seawater). The cooling water, whose temperature rises due to heat exchange with the air flowing in the main pipe 51, is cooled by the second water-cooled heat exchanger 90B after leaving the first water-cooled heat exchanger 90A and then flows back to the first water-cooled heat exchanger 90A.

[0101] exist Figure 3 In the second configuration shown in (b), as a countermeasure against temperature rise, a cooling water passage 100 is provided in the housing 31 of the rotary valve 30, from the air inlet 31A side to the outlet 31B side. In the passage 100, one end of a cooling water pipe 101 is connected to the cooling water inlet 100A on the inlet 31A side, and the other end of the cooling water pipe 101 is connected to the cooling water outlet 100B on the outlet 31B side. Cooling water flows through the passage 100 in the housing 31 to cool the rotary valve 30, thereby suppressing the temperature rise of the rotary valve 30 caused by the inflow of hot air.

[0102] Cooling water pipe 101 passes through water-cooled heat exchanger 102. Cooling seawater pipe 103 for cooling seawater (cooling seawater) is provided in water-cooled heat exchanger 102. Cooling water whose temperature has risen due to heat exchange with air flowing in rotary valve 30 flows out from cooling water outlet 100B to cooling water pipe 101, is cooled by water-cooled heat exchanger 102 and flows back into channel 100 from cooling water inlet 100A.

[0103] Further, by using the second water-cooled heat exchanger 90B or the water-cooled heat exchanger 102, it is possible to prevent the elution of a scale component and corrosion of the first water-cooled heat exchanger 90A or the housing 31 caused by seawater (cooling seawater), and it is possible to ensure the reliability of the complex structure of the rotary valve 30 or the surrounding structure. In addition, when the elution of a scale component of the second water-cooled heat exchanger 90B or the water-cooled heat exchanger 102 is intensified, by replacing the second water-cooled heat exchanger 90B or the water-cooled heat exchanger 102, it is possible to avoid replacement of the rotary valve 30 or the surrounding structure.

[0104] Further, although not illustrated, the cooling unit can be configured as follows in addition to the above-described first and second configuration examples.

[0105] Third configuration example: The basic structure is the same as that of the first configuration example, but the water-cooled heat exchanger (corresponding to the first water-cooled heat exchanger 90A) provided in the main pipe 51 on the upstream side of the rotary valve 30 is provided with a cooling seawater circulation pipe through which seawater flows, and differs from the first configuration example in that seawater is used instead of fresh water as cooling water.

[0106] Fourth configuration example: As the cooling unit, an air-cooled heat exchanger is provided in the main pipe 51 on the upstream side of the rotary valve 30, and air supplied from the air supply unit 20 is cooled while passing through the air-cooled heat exchanger and enters the rotary valve 30, thereby suppressing an increase in the temperature of the rotary valve 30.

[0107] Fifth configuration example: As the cooling unit, a fan that blows air or the like into the main pipe 51 on the upstream side of the rotary valve 30 is provided, and air supplied from the air supply unit 20 is cooled while passing through the position where the fan is provided and enters the rotary valve 30, thereby suppressing an increase in the temperature of the rotary valve 30.

[0108] Sixth configuration example: As the cooling unit, a cooling water pipe through which cooling water flows is provided in the vicinity of the main pipe 51 on the upstream side of the rotary valve 30, and air supplied from the air supply unit 20 is cooled while passing through the position where the cooling water pipe is provided and enters the rotary valve 30, thereby suppressing an increase in the temperature of the rotary valve 30. Further, the cooling water pipe can be arranged so as to be wound around the outer periphery of the main pipe 51.

[0109] Seventh configuration example: As the cooling unit, a cooling water injection pipe is connected to the main pipe 51 on the upstream side of the rotary valve 30, and air supplied from the air supply unit 20 is cooled by cooling water sprayed from the cooling water injection pipe and enters the rotary valve 30.

[0110] Eighth configuration example: As the cooling unit that cools the rotary valve 30, a fan that blows air or the like into the housing 31 is provided, thereby suppressing an increase in the temperature of the rotary valve 30.

[0111] Ninth configuration example: As the cooling unit, a cooling water tank having a water-cooled heat exchanger is provided, and the main pipe 51 on the upstream side of the rotary valve 30 passes through the cooling water tank, and the air supplied from the air supply unit 20 is cooled when passing through the installation site of the cooling water tank and enters the rotary valve 30, thereby suppressing the temperature rise of the rotary valve 30. In the water-cooled heat exchanger in the cooling water tank, an in-tank cooling water circulation pipe for flowing cooling water such as seawater is provided, and the cooling water flowing in the cooling water circulation pipe is cooled by another water-cooled heat exchanger or an air-cooled heat exchanger provided outside the tank.

[0112] As such, as a countermeasure against the temperature rise of the rotary valve 30 caused by the supply of the warmed air from the air supply unit 20, by adopting at least one of the cooling unit and the temperature rise countermeasure configuration, the performance reduction such as the increase in leakage of the rotary valve 30 can be prevented.

[0113] In the housing 31, a chamber (air chamber) 31C is provided between the inlet 31A and the rotary circular plate 32. In addition, Figure 2 The chamber 31C illustrated is gradually enlarged in shape from the upstream side to the downstream side, but can also be a chamber having substantially the same diameter from the upstream side to the downstream side.

[0114] By providing the chamber 31C in this way, the internal space of the rotary circular plate 32 of the housing 31 on the upstream side is configured to have a predetermined volume, and the equalization of the air entering from the inlet 31A is achieved, so that the pressure variation of the rotary valve 30 and the pipe path 50 can be suppressed. In addition, the internal pressure in the rotary valve 30 can be maintained at a pressure within a predetermined range, and the quantitative intermittent blowing from each air blowing outlet 10 can be performed.

[0115] The drive unit 36 is a motor whose rotational speed is variable, and the drive speed for rotating the rotary circular plate 32 can be changed.

[0116] The control unit 40 performs mode setting according to the blowing mode of the air, and controls the rotational speed of the rotary circular plate 32 by changing the drive speed of the drive unit 36. By changing the blowing period by changing the rotational speed of the rotary circular plate 32, the air can be blown at a period corresponding to each mode.

[0117] In addition, in the mode setting, in addition to the mode in which the air is periodically blown at a standard period, there are modes in which the air is periodically blown at a period longer than the standard period, a mode in which the air is periodically blown at a period shorter than the standard period, and the like.

[0118] Figure 4 is a diagram showing the overlap of the rotary circular plate aperture and the fixed circular plate aperture.

[0119] Four fixed circular plate openings 33A of a perfect circle are formed at 90-degree intervals in the circumferential direction of the fixed circular plate 33, and in contrast, one elongated rotating circular plate opening 32A is formed over the entire 1 / 4 of the rotating circular plate 32 (0 to 90 degrees). In this way, by providing the single rotating circular plate opening 32A in a shape that overlaps at least one of the plurality of fixed circular plate openings 33A regardless of the rotation angle of the rotating circular plate 32, it is possible to configure such that the rotating circular plate opening 32A is in communication with a certain branch pipe 52 regardless of the rotation angle of the rotating circular plate 32.

[0120] As described above, the air lubrication system can also be configured to use a solenoid valve, but in this case, there is concern that the abnormal increase in the transient solenoid valve internal pressure accompanying the opening and closing of the solenoid valve will occur. In contrast, the rotating valve 30 of the periodic air blowing air lubrication system of the present embodiment rotates the rotating circular plate opening 32A to overlap a certain fixed circular plate opening 33A during the periodic blowing of air, and thus is always in a state of communication with the branch pipe 52 that is a pressure release passage, and thus prevents the internal pressure from excessively increasing, and can suppress the increase in the rotation torque and the increase in air leakage, etc. In addition, since the pipe path 50 does not become a closed state during the periodic blowing of air, the operation of the air supply unit 20 is stable.

[0121] Figure 5 is a diagram showing the shape of the rotating circular plate opening, Figure 5 (a) of shows three examples of the shape of the rotating circular plate opening, Figure 5 (b) of shows the flow rate change of one air blowout port during the periodic blowing, for each example of the shape of the rotating circular plate opening.

[0122] The rotating circular plate opening 32A can also be provided in a shape other than that shown in Figure 4 . Figure 5 (a) of shows an example of the shape of the rotating circular plate opening 32A in which the outer edge and the inner edge have the same curvature and the both ends are straight lines, an example of the shape of the rotating circular plate opening 32A in which the outer edge and the inner edge have the same curvature and the both ends are curved lines, and an example of the shape of the rotating circular plate opening 32A in which the outer edge has a smaller curvature than the inner edge and the both ends are curved lines.

[0123] Figure 5 The line a in (b) of Figure 5 shows the flow rate change in the case of the rotating circular plate opening 32A on the left side of (a), the line β shows the flow rate change in the case of the rotating circular plate opening 32A in the center of (a), and the line γ shows the flow rate change in the case of the rotating circular plate opening 32A on the right side of (a). As shown in (b) of Figure 5 , the peak duration of the air flow rate in one port 31B can differ depending on the shape of the rotating circular plate opening 32A. Figure 5 Figure 5 ​​

[0124] The rotary valve 30 is configured to be able to adjust the duty ratio. The duty ratio is the ratio of the time of air blowing from the air blowing outlet 10 to the time of blowing stop, for example, if the time of blowing air is 25% and the time of stop is 75% in one cycle, the duty ratio is 0.25.

[0125] In order to enable adjustment of the duty ratio, for example, the rotary valve 30 is configured to be able to replace the rotary circular plate 32, and a plurality of rotary circular plates 32 having different shapes of rotary circular plate apertures 32A are prepared. Since the duty ratio changes depending on the shape of the rotary circular plate aperture 32A, by replacing the rotary circular plate 32 having a rotary circular plate aperture 32A of a certain shape with a rotary circular plate 32 having a rotary circular plate aperture 32A of another shape, the duty ratio can be changed.

[0126] In addition, Figure 6 is a drawing showing another example of a structure capable of adjusting the duty ratio, Figure 6 (a) of (a) shows a rotary valve provided with an adjustment circular plate, Figure 6 (b) of (a) shows a state in which the rotary circular plate aperture and the adjustment circular plate aperture partially coincide, Figure 6 (c) of (a) shows an example of a combination method of the rotary circular plate and the adjustment circular plate, Figure 6 (d) of (a) shows another example of a combination method of the rotary circular plate and the adjustment circular plate.

[0127] In this example, an adjustment circular plate 60 for adjusting the duty ratio is provided in a manner facing opposite to the side of the fixed circular plate 33 opposite to the side of the rotary circular plate 32. The adjustment circular plate 60 is as large as the rotary circular plate 32 and has an adjustment circular plate aperture 60A, and an adjustment circular plate shaft hole 60B for the shaft 35A to pass through is formed in the center portion. The adjustment circular plate aperture 60A is also an elongated shape like the rotary circular plate aperture 32A, and the size is also the same as the rotary circular plate aperture 32A. In addition, the adjustment circular plate aperture 60A can also have a shape and size different from the rotary circular plate aperture 32A.

[0128] The rotation angle of the rotary circular plate 32 and the adjustment circular plate 60 can be set at a predetermined interval, for example, every 30 degrees, and at the time of change, the rotary valve 30 is disassembled and fixed with a positioning pin or a pin or the like at the changed rotation angle.

[0129] By making the rotation angle of the adjustment circular plate 60 different from the rotation angle of the rotary circular plate 32 and blocking a part of the rotary circular plate aperture 32A with the adjustment circular plate 60, the duty ratio can be changed, for example, as shown in Figure 6The illustrated half of the duty ratio is set to the case where the rotating circular plate 32 is used alone. Further, since the size of the overlapping hole formed by the overlapping of the rotating circular plate hole 32A and the adjusting circular plate hole 60A can be changed according to the degree of overlapping of the rotating circular plate hole 32A and the adjusting circular plate hole 60A, the duty ratio can be changed by changing the size of the overlapping hole by changing the position (rotation angle) of the adjusting circular plate 60.

[0130] For example, Figure 6 (c) of the above-described (a) is an example in which a single rotating circular plate key groove 32F is provided on the periphery of the rotating circular plate shaft hole 32B of the rotating circular plate 32, and a plurality of adjusting circular plate key grooves 60C are provided on the periphery of the adjusting circular plate shaft hole 60B of the adjusting circular plate 60. According to which of the adjusting circular plate key grooves 60C is aligned with the position of the rotating circular plate key groove 32F, the size of the overlapping hole changes, so the duty ratio can be changed by selecting the adjusting circular plate key groove 60C that is fixed together with the rotating circular plate key groove 32F.

[0131] Further, Figure 6 (d) of the above-described (a) is an example in which a single rotating circular plate key groove 32F for preventing idling is provided on the periphery of the rotating circular plate shaft hole 32B of the rotating circular plate 32, and a plurality of pin holes 32G are provided at positions where the rotating circular plate hole 32A is not provided, and a single pin 60D is provided at a position where the adjusting circular plate shaft hole 60B is not provided in the adjusting circular plate 60. According to which of the pin holes 32G the pin 60D is inserted into, the size of the overlapping hole changes, so the duty ratio can be changed by selecting the pin hole 32G into which the pin 60D is inserted.

[0132] Further, Figure 7 is a diagram showing an example of a structure that can automatically adjust the duty ratio. As a structure that automatically controls and adjusts the duty ratio from the outside, a structure in which, for example, as shown in Figure 6 the adjusting circular plate 60, the rotating circular plate 32, and the fixed circular plate 33 are overlapped, a stepping motor 70 is built into the shaft 35A, and the position (rotation angle) of the adjusting circular plate 60 is controlled by an external signal to adjust the overlapping hole. In this case, the stepping motor 70 stops the rotation of the adjusting circular plate 60 when a prescribed overlapping hole is obtained, and fixedly maintains the position. Further, by driving the rotating circular plate 32 with the driving unit 36, the adjusting circular plate 60 also maintains the size of the overlapping hole and rotates together. A slip ring 71 that supplies power to the stepping motor 70 is provided in the shaft 35A, and the stepping motor 70 is covered by a protective case 80 made of a part of the shaft 35A. Further, an AC power source is connected to the driving unit 36, and a DC power source is connected to the slip ring 71.

[0133] In Figure 6In the present embodiment, an example is shown in which the adjustment circular plate 60, the rotating circular plate 32, and the fixed circular plate 33 are overlaid in this order, but the rotating circular plate 32 and the adjustment circular plate 60 can be exchanged, and overlaid in the order of the rotating circular plate 32, the adjustment circular plate 60, and the fixed circular plate 33, that is, the adjustment circular plate 60 is provided between the rotating circular plate 32 and the fixed circular plate 33. Further, as such an order, the size of the overlap hole formed by the overlap of the adjustment circular plate hole 60A of the adjustment circular plate 60 and the fixed circular plate hole 33A of the fixed circular plate 33 can be changed by rotating the adjustment circular plate 60. In this case, the adjustment circular plate 60 is fixedly held by the stepping motor 70 after the position (rotation angle) is adjusted in order to adjust the size of the overlap hole, and only the rotating circular plate 32 is rotated.

[0134] Further, even if configured so that the rotation axes of the rotating circular plate 32 and the adjustment circular plate 60 are double axes and the rotation angle can be changed by the stepping motor 70, the control of the duty ratio can be performed from the outside. In addition, as a unit that drives the adjustment circular plate 60, a servo motor or a solenoid, or the like can be used in addition to the stepping motor 70.

[0135] In addition, the shape of the adjustment circular plate 60 can be any shape other than a circle that can function.

[0136] As such, the rotating valve 30 is configured to be able to adjust the duty ratio that is the ratio of the time of air blowing from the air blowing outlet 10 to the time of blowing stop. The control unit 40 performs mode setting according to the blowing mode of air, and changes the control of the duty ratio, for example, by changing the rotation angle of the rotating circular plate 32 and the adjustment circular plate 60. The control of the duty ratio set in the rotating valve 30 according to the mode is performed by the control unit 40, so that the blowing interval can be changed according to the sailing condition of the ship 1, and the reduction of frictional resistance based on air lubrication can be effectively performed.

[0137] Figure 8 is a view showing other examples of the rotating circular plate, Figure 8 (a) of FIG. 1 shows the rotation angle when continuous blowing is performed, Figure 8 (b) of FIG. 1 shows the rotation angle when periodic blowing is performed.

[0138] In the present embodiment, with respect to the fixed circular plate 33 in which four regular circular fixed circular plate holes 33A are formed at 90-degree intervals on the outer circumferential side, one elongated rotating circular plate hole 32A that extends over 3 / 4 of the circumference (0 to 270 degrees) is formed on the outer circumferential side of the rotating circular plate 32. Further, the minor diameter of the rotating circular plate hole 32A is preferably set to be larger than the diameter of the fixed circular plate hole 33A, and in the present embodiment, is set to be larger than the diameter of the fixed circular plate hole 33A.

[0139] In the periodic blowing mode, as shown in Figure 8As shown in (b) of FIG. 6, the control unit 40 rotates the rotating circular plate 32 in one direction in such a manner that the rotating circular plate aperture 32A overlaps with three fixed circular plate apertures 33A and does not overlap with one fixed circular plate aperture 33A, thereby sequentially stopping the supply of air to one branch pipe 52, and periodic blowing can be performed.

[0140] On the other hand, in the continuous blowing mode, as shown in (a) of FIG. 7, the control unit 40 stops the rotation of the rotating circular plate 32 in a state in which the rotating circular plate aperture 32A overlaps with two fixed circular plate apertures 33A and overlaps with the remaining two fixed circular plate apertures 33A by half, thereby continuously supplying air to all of the branch pipes 52, and continuous blowing from all of the air blow outlets 10 can be performed. Figure 8

[0141] As such, by configuring the rotating circular plate aperture 32A to have a rotation angle that overlaps with all of the plurality of fixed circular plate apertures 33A, by adjusting the rotation angle of the rotating circular plate 32, the plurality of fixed circular plate apertures 33A that guide air to the plurality of outlets 3 IB are connected, and the configuration is such that air can be continuously blown, and thus periodic blowing and continuous blowing can be switched by one rotary valve 30 by selection of the mode.

[0142] Figure 9 FIG. 8 is a view that shows another other example of a rotating circular plate.

[0143] In this example, two rotating circular plates 32 are provided. With respect to the fixed circular plate 33 in which four circular fixed circular plate apertures 33A are formed at 90-degree intervals in the circumferential direction, one elongated rotating circular plate aperture 32A that extends over ¼ of the circumference (0 to 90 degrees) is formed in each of the two rotating circular plates 32. In addition, the minor diameter of the rotating circular plate aperture 32A is set to be larger than the diameter of the fixed circular plate aperture 33A.

[0144] The control unit 40 rotates the rotating circular plate aperture 32A of one rotating circular plate 32 in a state in which it overlaps with the rotating circular plate aperture 32A of the other rotating circular plate 32 in the periodic blowing mode. On the other hand, in a state in which the rotating angle of one rotating circular plate 32 is offset by 180 degrees from the rotating angle of the other rotating circular plate 32, and the like, the rotating circular plate aperture 32A of one rotating circular plate 32 does not overlap with the rotating circular plate aperture 32A of the other rotating circular plate 32 at the time of stopping the operation of the air supply unit 20, thereby blocking all of the branch pipes 52.

[0145] ​In this way, the rotary valve 30 has a structure capable of blocking all of the plurality of branch pipes 52, and the control unit 40 controls the rotary valve 30 to block all of the branch pipes 52 by adjusting the rotation angle of the rotary circular plate 32 at the time of stopping the operation of the air supply unit 20, and controls the rotation angle of the rotary circular plate 32 to block the air flow to the branch pipes 52 at the time of non-blowing, so that water does not flow back to all of the branch pipes 52 from the air blowout port 10 or marine organisms do not intrude.

[0146] Further, it is also possible to configure the rotary circular plate opening 32A of one rotary circular plate 32 to be formed in a manner that does not overlap with any of the plurality of fixed circular plate openings 33A in the rotation angle, and to block the plurality of fixed circular plate openings 33A by adjusting the rotation angle of the rotary circular plate 32 to stop the blowing of air. In this configuration, at the time of non-blowing, it is also possible to block all of the fixed circular plate openings 33A by adjusting the rotation angle of the rotary circular plate 32 to block the outlet 31B and block the air flow to the branch pipes 52.

[0147] Figure 10 is a diagram showing a control method for the rotary circular plate in the case where the ship generates a prescribed or greater roll, Figure 10 (a) of FIG. 1 shows a control in the case where the roll is “large”, Figure 10 (b) of FIG. 1 shows a control in the case where the roll is “medium”.

[0148] The rotary circular plate 32 is formed with one elongated rotary circular plate opening 32A that extends over ¼ of a circle (0 to 90 degrees), and the fixed circular plate 33 is formed with four fixed circular plate openings 33A that are regular circles at 90-degree intervals in the circumferential direction.

[0149] If the four fixed circular plate openings 33A are a first fixed circular plate opening 33Aa, a second fixed circular plate opening 33Ab, a third fixed circular plate opening 33Ac, and a fourth fixed circular plate opening 33Ad, then the first fixed circular plate opening 33Aa and the fourth fixed circular plate opening 33Ad are connected to the air blowout port 10 provided near the ship side, and the second fixed circular plate opening 33Ab and the third fixed circular plate opening 33Ac are connected to the air blowout port 10 provided near the ship center.

[0150] In the case where the roll of the ship 1 is large, the air blowout port 10 provided near the ship center is always in water, but the air blowout port 10 provided near the ship side sometimes becomes a state of being exposed from the water. Therefore, the control unit 40, in the case where the degree of roll is “large”, controls the rotary circular plate 32 to block the air flow to the branch pipes 52 by adjusting the rotation angle of the rotary circular plate 32 to block all of the branch pipes 52, and controls the rotation angle of the rotary circular plate 32 to block the air flow to the branch pipes 52 at the time of non-blowing, so that water does not flow back to all of the branch pipes 52 from the air blowout port 10 or marine organisms do not intrude. Figure 10As shown in (a), the rotating circular plate 32 is rotated clockwise and counterclockwise within a range of 90 degrees, such that the first fixed circular plate opening 33Aa and the fourth fixed circular plate opening 33Ad are always closed, while the second fixed circular plate opening 33Ab and the third fixed circular plate opening 33Ac are alternately opened and closed. This allows air to be periodically blown out from the air outlet 10 connected to the second fixed circular plate opening 33Ab and the air outlet 10 connected to the third fixed circular plate opening 33Ac. By configuring the air outlet 10, which is located near the center of the hull and is also in the water during periods of high roll, the reduction in frictional resistance reduction based on air lubrication can be suppressed.

[0151] Additionally, when the roll level is "medium", the control unit 40, such as Figure 10 As shown in (b), the rotating disc 32 is rotated in both directions within a 180-degree range, causing the first fixed disc opening 33Aa and the second fixed disc opening 33Ab, and the third fixed disc opening 33Ac and the fourth fixed disc opening 33Ad to open and close alternately. This reduces the flow rate in each air outlet 10 while alternately switching between the third fixed disc opening 33Ac and the fourth fixed disc opening 33Ad connected to the air outlet 10 located to the left of the hull center, and the first fixed disc opening 33Aa and the second fixed disc opening 33Ab connected to the air outlet 10 located to the right of the hull center, allowing for periodic blowing using all air outlets 10. Furthermore, depending on the shape of the rotating disc opening 32A, a structure that does not reduce the flow rate in the air outlet 10 can also be adopted. Alternatively, the first fixed circular plate opening 33Aa and the second fixed circular plate opening 33Ab, as well as the third fixed circular plate opening 33Ac and the fourth fixed circular plate opening 33Ad, can be alternately opened and closed by rotating in one direction instead of rotating in the opposite direction.

[0152] In this way, the rotary valve 30 has a structure that can select a specified branch pipe 52 from a plurality of branch pipes 52. The control unit 40 controls the rotation of the rotary disc 32 or the forward and reverse rotation according to the mode setting of the air blowing mode to periodically supply air from the specified air outlet 10. It can distribute air to the selected specified branch pipe 52 and perform periodic blowing corresponding to each mode.

[0153] In addition, the degree of sway can be determined, for example, by comparing sensor values ​​with a threshold.

[0154] Figure 11 This diagram illustrates other control methods for the rotating disc when the ship experiences a roll exceeding a specified limit.

[0155] In the present control method, the control unit 40 fixes the rotation angle of the rotating circular plate 32 so that the first fixed circular plate aperture 33Aa and the fourth fixed circular plate aperture 33Ad are always closed and the second fixed circular plate aperture 33Ab and the third fixed circular plate aperture 33Ac are always open in the case where the degree of roll is "large".

[0156] Thus, air can be continuously blown out from the air blowout port 10 connected to the second fixed circular plate aperture 33Ab and the air blowout port 10 connected to the third fixed circular plate aperture 33Ac.

[0157] As such, the rotary valve 30 has a structure capable of selecting a prescribed branch duct 52 among a plurality of branch ducts 52, and the control unit 40 can be set to continuous blowout corresponding to the mode by performing control to supply air from the prescribed air blowout port 10 by stopping the rotation of the rotating circular plate 32 in accordance with the mode setting of the air blowout mode.

[0158] Figure 12 is a view showing another other example of a rotating circular plate, Figure 12 (a) of FIG. 1 shows a rotating circular plate in which an anti-eccentricity aperture is formed on the diagonal side of the rotating circular plate aperture, Figure 12 (b) of FIG. 1 shows a rotating circular plate in which a counterbore process (non-through hole process) is applied to the diagonal side of the rotating circular plate aperture, Figure 12 (c) of FIG. 1 shows a rotating circular plate in which a counterweight is attached along the outer edge of the rotating circular plate aperture.

[0159] The rotating circular plate aperture 32A formed only at one side at a position apart from the center portion of the rotating circular plate 32 can become a cause of eccentricity. Therefore, in order to prevent eccentricity of the shaft accompanying rotation caused by the eccentricity of the rotating circular plate aperture 32A, it is preferable to take the following countermeasures: as shown in Figure 12 (a) of FIG. 1, an anti-eccentricity aperture 32C of the same shape is provided at the symmetric position of the rotating circular plate aperture 32A, or as shown in Figure 12 (b) of FIG. 1, an anti-eccentricity counterbore process 32D of an approximate shape is applied to the symmetric position of the rotating circular plate aperture 32A, or as shown in Figure 12 (c) of FIG. 1, a counterweight 32E is provided in the vicinity of the rotating circular plate aperture 32A. By applying any one of the anti-eccentricity aperture 32C, the anti-eccentricity counterbore process 32D, or the counterweight 32E, it is possible to prevent eccentricity of the shaft when the rotating circular plate 32 rotates.

[0160] Figure 13 is a view of a cycle blowout test using a model, Figure 13 (a) of FIG. 1 shows a test result, Figure 13 (b) of FIG. 1 shows a situation in the test.

[0161] In order to verify the present application, a test using a model was carried out. The rotary path switching unit 30 used in the test was a rotary valve provided with a rotating circular plate 32 serving as a valve body formed with one elongated rotating circular plate aperture 32A extending over 1 / 4 of a circle (0 to 90 degrees) and a fixed circular plate 33 formed with four circular fixed circular plate apertures 33A at 90-degree intervals in the circumferential direction, and the test conditions were set to an air flow rate Q of 100 [L / min] supplied from a drive unit (motor) 36 and a rotational speed n of the rotating circular plate 32 of 2 [rps] (= 0.5 [Hz]).

[0162] In Figure 13 In (a) of FIG. 8, Q1 to Q4 are the respective mass flow rates of the four air blow outlets 10, and Q is the overall mass flow rate. The results of the test, as shown in (a) of FIG. 8, confirmed that periodic blow-off of 0.5 Hz or less was possible, and that substantially uniform intermittent blow-off from each of the air blow outlets 10 was confirmed. Figure 13

[0163] Industrial applicability The periodic blow-off air lubrication system according to the present application can perform switching to a plurality of blow-off methods and duty ratio control, and by using periodic blow-off, it is possible to increase the friction resistance reduction effect based on air lubrication while suppressing the power used for air blow-off.

[0164] The periodic blow-off air lubrication system according to the present application and the rotary valve for a periodic blow-off air lubrication system can be applied not only to air lubrication methods in actual ships but also to tests of air lubrication methods using models.

[0165] Explanation of reference numerals 1 ship 10 air blow outlet 20 air supply unit 30 rotary path switching unit (rotary valve for a periodic blow-off air lubrication system) 31 housing 31A inlet 31B outlet 32 rotating circular plate 32A rotating circular plate aperture 32C eccentricity-preventing aperture 32D counterbore machining 32E counterweight 33 fixed circular plate 33A fixed circular plate aperture 34 force application unit 35A shaft 36 drive unit 40 control unit ​50 pipe path 52 branch pipe 60 adjusting disc 60A adjusting disc opening 90A cooling unit 100 cooling unit (passage of cooling water)

Claims

1. A periodic air blowing lubrication system which is an air lubrication system that periodically blows air toward the bottom of a ship to reduce the frictional resistance of the ship body, characterized by, Possessing: a plurality of air blow outlets provided to the ship bottom; an air supply unit that supplies air to the plurality of air blow outlets via a pipe path; a rotary path switching unit provided midway in the pipe path; and a control unit that controls the rotary path switching unit, has a plurality of branch pipes on the downstream side of the rotary path switching unit as the pipe path to the plurality of air blow outlets, switches the air blow outlets to which the air is supplied in a prescribed order by rotation of a valve body of the rotary path switching unit, and is able to periodically blow the air from all of the plurality of air blow outlets by rotation of the valve body of the rotary path switching unit.

2. The periodic air-blowing lubrication system according to claim 1, wherein The rotary path switching unit is configured to communicate with a certain one of the branch pipes regardless of the rotation angle of the valve body.

3. The periodic air-blowing lubrication system of claim 1, wherein, The rotary path switching unit is configured to be able to adjust a duty cycle that is a ratio of time during which the air is blown from the air blow outlets to time during which blowing is stopped, and the control unit performs mode setting according to a blowing mode of the air and changes control of the duty cycle by rotation of the valve body.

4. The periodic air-blowing lubrication system of claim 1, wherein, The control unit performs control that changes the rotation speed of the valve body of the rotary path switching unit according to mode setting of the blowing mode of the air.

5. The periodic air-blowing lubrication system of claim 1, wherein, The rotary path switching unit has a structure that is able to communicate all of the plurality of branch pipes, and the control unit performs control that adjusts the rotation angle of the valve body of the rotary path switching unit to continuously blow the air from all of the air blow outlets according to mode setting of the blowing mode of the air.

6. The periodic air-blowing lubrication system of claim 1, wherein, The rotary path switching unit has a structure that is able to block all of the plurality of branch pipes, and the control unit performs control that adjusts the rotation angle of the valve body of the rotary path switching unit to block all of the branch pipes when operation of the air supply unit is stopped.

7. The periodic air-blowing lubrication system of claim 1, wherein The rotary path switching unit has a structure that is able to select a prescribed one of the plurality of branch pipes, and the control unit performs control that periodically supplies the air from a prescribed air blow outlet by rotating or rotating in reverse the valve body according to mode setting of the blowing mode of the air.

8. The periodic air-blowing lubrication system of claim 2, wherein, The rotary path switching unit has a structure that is able to select a prescribed one of the plurality of branch pipes, and the control unit performs control that supplies the air from a prescribed air blow outlet by stopping rotation of the valve body according to mode setting of the blowing mode of the air.

9. The periodic air-blowing lubrication system of claim 1, wherein, Temperature rise of the rotary path switching unit that occurs in association with supply of the air that has warmed up from the air supply unit is addressed by employing at least one of a cooling unit and a temperature rise countermeasure configuration.

10. A rotary valve for a periodic blow air lubrication system, which is used as a rotary type path switching unit of a periodic blow air lubrication system according to any one of claims 1 to 9, characterized by Possessing: a housing that has an air inlet and a plurality of outlets; a rotary circular plate that is a valve body, is housed in the housing, and has a single rotary circular plate aperture; a fixed circular plate that is a valve seat, allows the rotary circular plate to slide, and has a plurality of fixed circular plate apertures that guide the air to the plurality of outlets; a force applying unit that presses the rotating circular plate against the fixed circular plate; and a drive unit that rotationally drives the rotating circular plate via a shaft.

11. The rotary valve for a cyclic air-blowing lubrication system according to claim 10 when dependent on claim 2, characterized in that The single rotating circular plate hole is configured to overlap at least one of the plurality of fixed circular plate holes regardless of the rotation angle.

12. The rotary valve for a cyclic air-blowing lubrication system according to claim 10 when dependent on claim 3, characterized in that The rotating valve is configured to enable exchange of another rotating circular plate having another rotating circular plate hole different from the rotating circular plate hole of the valve body with the rotating circular plate, and to make the duty ratio variable.

13. The rotary valve for a cyclic air-blowing lubrication system according to claim 10 when dependent on claim 3, characterized in that An adjustment circular plate for adjusting the duty ratio is further provided, and the adjustment circular plate is configured to enable change of the overlap hole formed by overlap of the rotating circular plate hole and an adjustment circular plate hole of the adjustment circular plate, or overlap of the adjustment circular plate hole and the fixed circular plate hole, to make the duty ratio variable.

14. The rotary valve for a cyclic air-blowing lubrication system according to claim 10 when dependent on claim 4, characterized in that The drive unit that rotationally drives the rotating circular plate is configured to enable change of the drive speed.

15. The rotary valve for a cyclic air-blowing lubrication system according to claim 10 when dependent on claim 5, characterized in that The rotating circular plate hole is configured to have a rotation angle that overlaps all of the plurality of fixed circular plate holes by rotation of the rotating circular plate, and the plurality of fixed circular plate holes that guide the air to the plurality of outlets are communicated by adjustment of the rotation angle of the rotating circular plate, enabling continuous blowing out of the air.

16. The rotary valve for a cyclic air-blowing lubrication system according to claim 10 when dependent on claim 6, characterized in that The rotating circular plate hole is configured to have a rotation angle that does not overlap any of the plurality of fixed circular plate holes by rotation of the rotating circular plate, and the plurality of fixed circular plate holes that guide the air to the plurality of outlets are blocked by adjustment of the rotation angle of the rotating circular plate, enabling stopping of blowing out of the air.

17. The rotary valve for a cyclic air-blowing lubrication system according to claim 10 when dependent on claim 9, characterized in that At least one of a passage that provides cooling water that cools the rotating valve in the housing, and a degree of freedom in the axial direction of the rotating circular plate with respect to the shaft that applies force to the rotating circular plate against the fixed circular plate is adopted.

18. The rotary valve for a cyclical air-blowing lubrication system according to claim 10, characterized by To prevent eccentricity of the shaft that accompanies rotation caused by offset of the rotating circular plate hole, any of the following countermeasures is taken: a countermeasure of providing an anti-eccentricity hole of the same shape at a symmetrical position of the rotating circular plate hole of the rotating circular plate, a countermeasure of performing an anti-eccentricity counterbore process of an approximate shape at a symmetrical position of the rotating circular plate hole, or a countermeasure of providing a counterweight in the vicinity of the rotating circular plate hole.

19. The rotary valve for a cyclical air-blowing lubrication system according to claim 10, characterized by The internal space of the housing on the upstream side of the rotating circular plate is configured to have a prescribed volume, enabling equalization of the air that enters from the inlet.

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