WO2022114366A1 - Moteur à ailettes - Google Patents

Moteur à ailettes Download PDF

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Publication number
WO2022114366A1
WO2022114366A1 PCT/KR2020/018807 KR2020018807W WO2022114366A1 WO 2022114366 A1 WO2022114366 A1 WO 2022114366A1 KR 2020018807 W KR2020018807 W KR 2020018807W WO 2022114366 A1 WO2022114366 A1 WO 2022114366A1
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WO
WIPO (PCT)
Prior art keywords
vane
rotor
casing
pressure fluid
pressure
Prior art date
Application number
PCT/KR2020/018807
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English (en)
Korean (ko)
Inventor
최원석
Original Assignee
이엑스디엘 주식회사
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 이엑스디엘 주식회사 filed Critical 이엑스디엘 주식회사
Priority to JP2023532102A priority Critical patent/JP2023551252A/ja
Publication of WO2022114366A1 publication Critical patent/WO2022114366A1/fr
Priority to US18/200,758 priority patent/US20230287792A1/en

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/30—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F01C1/32—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in group F01C1/02 and relative reciprocation between the co-operating members
    • F01C1/321—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in group F01C1/02 and relative reciprocation between the co-operating members with vanes hinged to the inner member and reciprocating with respect to the inner member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/30—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F01C1/34—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members
    • F01C1/344—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F01C21/0809—Construction of vanes or vane holders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/18—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet

Definitions

  • the present invention relates to a vane motor, and more particularly, to a configuration capable of stably moving the vane in a groove in a vane motor capable of generating a rotational force through pneumatic pressure and effectively reducing wear of the vane.
  • a vane motor is one of the mechanical devices that converts fluid pressure into rotational power. 1 shows an example of a conventional vane motor.
  • a rotating rotor is installed in the casing 211 , and a part of the casing 211 has a fluid inlet 253 into which a fluid applying pressure is introduced and a fluid outlet 255 through which the fluid is discharged.
  • a pressure fluid is introduced into the fluid inlet 253
  • the fluid pressure extends to the outside of the rotor and acts on the vanes 235 whose extension length is variable. Accordingly, while the vane 235 moves in the pressure direction, the entire rotor rotates within the casing 211 .
  • the fluid that transmits the pressure to the vane 235 reaches the fluid outlet 255 of the case, the fluid is discharged through the low pressure fluid outlet 255 .
  • the vane 235 is coupled to the rotor body 231 , and the length of the vane 235 protruding from the body 231 may be variable. To this end, the vane 235 is inserted into the groove 231a of the rotor body 231 and can move in the groove 231a in the longitudinal direction of the groove.
  • an elastic body such as a spring may be included at the bottom of the groove between the vane and the vane.
  • a separate spring may not be installed because the vane may come out of the groove by the rotational centrifugal force of the rotor.
  • Republic of Korea Patent Registration No. 10-1199197 discloses a vane mechanism configured to change a flat vane to an arc type and form the center of the arc as a link so that the vane rotates and reciprocates.
  • This configuration is to solve the problems caused by the linear reciprocating motion of the flat vane, such as friction, wear of the vane, and the problem of vane operation abnormality.
  • the groove is filled with a pressure fluid by forming a groove that is too large, and the pressure of the pressure fluid filled in the groove is not always the same depending on the location. Therefore, when supplying the pressure fluid to the inlet, more pressure fluid must be supplied to make this space a high pressure, so the efficiency of the vane motor that can produce a large output with a small amount of pressure fluid can be reduced.
  • Korean Patent Application No. 10-2019-0171567 filed by the inventor of the present invention discloses a vane motor as shown in FIG. 2 in which a cylindrical inner cylinder is installed between the rotor and the casing to reduce wear and friction between the vane and the casing. .
  • the rotor which receives the pressure of the pressure fluid in the casing and rotates about the rotational shaft mounted on the casing, is installed in a groove formed on the side of the body and a cylindrical body as a whole having a central axis coincident with the rotational axis, and according to the rotational phase It has a vane of varying width protruding from the groove.
  • the casing is made in the form of a cylindrical closed container that closes both ends of the cylindrical outer cylinder accommodating the rotor with a closing plate, an inlet of the pressure fluid is installed in at least one of the closing plate, and the inlet of the pressure fluid is inside the cylindrical inner cylinder It is made in the form of an arc-shaped curve connected to the space outside the rotor body.
  • An object of the present invention is to provide a configuration that can reduce problems such as abnormal operation of the vanes, wear, friction, etc. resulting from the linear reciprocating motion of the vanes in the conventional vane motor described above.
  • a casing having an inlet and an outlet through which the pressure fluid is introduced and discharged;
  • a rotor configured to receive the pressure of the pressure fluid in the casing and rotate about a rotation shaft mounted on the casing
  • the rotor is installed in a vane guide groove formed on the side of the main body and the main body in a cylindrical shape having a central axis coincident with the rotation axis, and has a vane whose width protrudes from the vane guide groove according to the rotational phase,
  • the vane On the side view when viewed in the longitudinal direction of the axis of rotation, the vane forms an arc shape, the vane guide groove forms an arc-shaped groove to accommodate the vane, and the vane rotates on a part of the rotor body by a link rod installed on one side of the vane. It is characterized in that it is possible to be coupled.
  • a hinge for rotatably coupling the link rod to a portion of the rotor body may be used for the vane to be rotatably coupled to the rotor body through the link rod.
  • the link rod is coupled to the upper end of the vane, and the hinge shaft is installed on the surface layer of the rotor body, so that when the vane is maximally accommodated in the vane guide groove, a separate link rod accommodating groove is not installed on the rotor surface. , it is preferable to be formed in a minimum volume so that only the link rod is accommodated even when the receiving groove is installed.
  • the link rod has a thickness that is much smaller than the overall length or thickness of the rotor body (when the rotor is viewed as a thick disk rather than a cylinder), and the link rod is removed from the surface of the rotor body.
  • the accommodating groove is made so that the bottom of the groove can only be accommodated with a fine gap with the link rod in a range that does not directly collide with the link rod when the vane is accommodated in the vane guide groove.
  • the link rod may be installed in the longitudinal middle part or one or both ends of the longitudinal direction of the rotor, and accordingly, the hinge shaft may also be installed in the longitudinal middle part, one end or both ends of the rotor.
  • an enlarged part from which the rotor body is partially removed may be installed at the rear entrance based on the rotational direction from the entrance of the vane guide groove.
  • the lower end of the vane (the end at the center of the rotor) do not come out to the enlarged part even when the vane comes out as far as possible. Otherwise, the compressed fluid may leak into the space in front of the vane through the enlarged part under the lower end of the vane, weakening the pressure pushing the vane forward and lowering the vane efficiency.
  • a concave groove may be formed in the upper rear surface of the vane so that the pressure of the inlet air can act well on the vane.
  • the groove may simply be a concave groove in the forward direction, but when viewed from the side view, an acute-angled jaw is formed at the entrance toward the center of the groove (in the direction of the rotational axis of the rotor in the side view) so that a part of the groove forms a concave portion toward the center of the rotor. It is desirable to install it as much as possible.
  • the pressure of the inflow fluid acts on this groove and tends to cause the vane to enter the inside of the vane guide groove. It is in close contact with the wall and can play a role in preventing rotational obstruction that prevents it from sliding naturally on the inner wall.
  • one or a plurality of inlets of the pressure fluid may be distributed and installed, and are installed in the cylindrical body of the casing along the rotational direction, or are formed in the closing plate portion closing both ends of the cylindrical body of the casing, and the pressure fluid from the side toward the rotor It may be made to supply.
  • an elastic means for applying a restoring force to the outside (toward the casing inner wall) for the reciprocating operation of the vane for example, a spring may be installed, and the elastic means may be installed in the vane guide groove or installed around the hinge shaft.
  • the rotor is accommodated in the casing, and the end of the vane is made to contact the inner wall surface while holding the pressure fluid inside until the pressure fluid injected through the inlet of the casing is discharged through the casing outlet.
  • the casing covers the inner cylinder and the rotor, and is in the form of a cylindrical closed container having an approximately cylindrical body that can secure a space for the inner cylinder to rotate inside, and a portion or closing plate that closes both ends of the cylindrical body.
  • the finishing plate part is installed so that it is possible to slide (sliding) between both ends in the longitudinal direction (rotation axis direction) of the inner cylinder and in the parts in contact with both ends of the rotor body and the vane, and it is installed so that it has a fine gap through which pressure fluid is difficult to leak.
  • the outlet and inlet are installed on both or one side of the closing plate so that when they overlap with the space inside the cylindrical inner cylinder and outside the rotor body when viewed in the direction of the rotor rotation axis, the pressure fluid flows into or out of the space. can do.
  • the rotor is partially removed at the rear entrance of the vane guide groove to install the side extension, and the inlet of the pressure fluid is limited to the space where the side extension is installed and overlaps in a curved shape close to an arc on the finish plate, more precisely
  • the side extension may be installed according to a portion of the trajectory drawn while moving.
  • the side extension is connected to the space surrounded by the inner surface of the vane, the rotor, and the inner cylinder to form a part of the space.
  • the inlet may first meet at a position where a space or a gap is created between the rotor and the inner cylinder when the rotor rotates and begins to widen further.
  • the vane motor of the present invention when the pressure fluid inlet is provided with a plurality of holes arranged, the vane motor of the present invention includes a plurality of pressure fluid conduits (channels) connected to the plurality of holes one by one, and each of the plurality of pressure fluid conduits.
  • a separately formed opening/closing control means is provided, and the output or torque of the vane motor can be adjusted step-by-step (in multiple stages) through these opening/closing control means.
  • the vanes are formed in an arc shape, and the arc-shaped vanes rotate according to the arc trajectory instead of the linear reciprocating motion, so that problems such as abnormal operation of the vanes, wear, friction, etc. can be reduced.
  • FIG. 1 is a perspective view showing the configuration of a conventional vane motor
  • FIG. 2 is an exploded perspective view showing the configuration of another vane motor
  • FIG. 3 is an exploded perspective view of a first embodiment of the present invention.
  • FIG. 4 is a side cross-sectional view showing a cross section of the first embodiment of the present invention cut in a plane perpendicular to the axis of rotation;
  • FIG. 5 is a perspective view separately showing a vane coupled to the rotor body in the first embodiment of the present invention
  • Figure 6 is a partial side view showing the pressure intensifying groove installed on the upper rear surface of the vane in the first embodiment of the present invention in comparison with the pressure increasing groove that can be applied instead of it;
  • FIG. 7 is an exploded perspective view of a second embodiment of the present invention.
  • Fig. 8 is a perspective side view of a second embodiment of the present invention.
  • FIG. 9 is a perspective view showing a rotor comprising a combination of a rotor body and a vane in the second embodiment of the present invention.
  • the vane motor in this embodiment is made with a casing forming the outermost shell, and a rotor positioned in the casing, and except as specifically described herein, mostly of the existing casing and rotor. It can be done similarly to the configuration.
  • the casing includes a casing body 311 having a substantially cylindrical shape and finishing plates 313 and 315 for closing both ends of the casing body 311 in the longitudinal direction.
  • the rotor body 330 is formed in a cylindrical shape or a thick disk shape, and a vane guide groove 331a in which a vane 335 is installed is formed on the side of the cylinder.
  • the vane 335 is made of a thick plate shape having an arc shape
  • the vane guide groove 331a is made of a groove having an arc shape that can accommodate such a vane.
  • the vane 335 is connected to a part of the rotor body 330 by a link rod 337 installed on one side of the vane (the front side when considering the rotation direction), and this link rod 337 and the hinge shaft 339 ) is rotatably coupled to the rotor body.
  • the link rod 337 and the hinge shaft 339 are not formed over the entire length or thickness of the rotor (when the rotor body is viewed as a thick disk), but may be formed over a partial thickness, where in the middle part in the direction of the rotation axis of the rotor It is formed to be thinner than the rotor thickness.
  • the link rod 337 is coupled to the upper end of the vane 335 (outermost relative to the rotational center axis of the rotor), and the hinge shaft 339 is installed on the surface layer (outer layer) of the rotor body 330 .
  • the link rod accommodating groove 331c installed in the longitudinal middle portion of the rotor body is formed to a minimum depth to facilitate installation and minimize the volume occupied by the link rod.
  • the link rod accommodating groove 331c has a little extra depth so that the link rod 337 does not directly collide with the rotor body to generate vibration when the vane moves, and the vane guide groove also has a little extra depth. It is desirable to have a depth.
  • the link rod 337 may be installed only at one end of the rotor body in the direction of the axis of rotation, or at the other end, so that the two may be installed symmetrically at both ends in the direction of the axis of rotation, in this case, more stably reciprocating angular motion
  • the vanes can be supported on the rotor so that
  • the rotor body portion at the rear of the rotor body at the entrance of the vane guide groove in the rotational direction is the rotor body.
  • the surface and the groove form an acute angle
  • the part of the rotor body at the rear at the entrance of the vane guide groove is partially removed to form a smooth and gentle curve like a round treatment. This may be seen as installation of the extension 331b by a kind of chamfer.
  • the separation space surrounded by the vane rear surface, the casing inner wall surface, and the rotor body surface is formed larger, meets the pressure fluid inlet faster than in the case without the extension, and more vanes Expose the rear face to allow pressure to be applied through a larger area of the rear face of the vane.
  • the lower end (the end of the center of the rotor) of the vane 337 prevents the vane 337 from coming out to the extended part 331b even when the vane 337 comes out as far as possible. If the lower end of the vane meets the extension, the compressed fluid leaks into the space in front of the vane through the extension under the lower end of the vane, and the pressure in the front space increases and the pressure in the rear space decreases, and the pressure pushing the vane forward is weakened. The vane efficiency is lowered.
  • a rotation shaft installation hole 351 through which a rotation shaft connected to the rotor is mounted or passed is installed in the finishing plates 313 and 315 .
  • the rotating shaft may be integrally formed with the rotor body 330 .
  • the pressure fluid inlet and the pressure fluid outlet are formed on the side wall of the substantially cylindrical part, which is the casing body 311 , and the pressure fluid inlet 355 into which the external high-pressure fluid is input is provided with four holes 355a, 355b, 355c, 355d. ), and the pressure fluid outlet 353 is also divided into two holes 353a and 353b. They are arranged in a circumferential direction when viewed from the side view, and as the rotor rotates, they meet in turn with each compartment surrounded by the vane, the rotor body and the casing.
  • a bearing is installed on the finish plate in which the rotation shaft installation hole is formed, so that the rotation shaft does not come into direct contact with the finish plate 313 , and friction during rotation can be reduced by the bearing.
  • the rotor rotates while in contact with the inner surface of the casing body 311 .
  • the position of the first hole (355a) where each vane first meets when considering the rotation direction among the holes that are divided into four and constitute the pressure fluid inlet is that the vane 337 is completely in the vane guide groove (331a) when the rotor rotates ( Or at the maximum), a space or a gap between the rotor and the inner surface of the casing body starts to form, and the vane can also be moved outward.
  • the partition space increases in volume as the vane 337 exits further to the outer side according to the rotation of the rotor and the space between the rotor and the inner surface of the casing increases, and this partition space is sequentially formed by the second hole (355b) and the third hole (355c) , while meeting the fourth hole 355d, the pressure fluid may be continuously supplied. Accordingly, a considerable high pressure can be maintained despite the expansion of the compartment space, and the pressure of the high-pressure fluid inside the compartment space can continue to act on the rear surface of the vane, and a torque that turns the rotor clockwise can be applied.
  • the maximum pressure acts on the partition space meeting the first hole 311a and the In the separation space at the front, the pressure by the pressure fluid is sequentially reduced in turn, and a torque that causes the rotor to rotate in a clockwise direction is applied to each vane, and the torque or output can be transmitted to the outside by the rotating shaft of the rotor.
  • a concave pressure intensifying groove 336 for changing the thickness of the vane is also formed on the upper rear surface of the vane 337 here.
  • the concave pressure enhancing groove 336 is concavely formed in the front surface direction of the vane over the entire length when viewed in the longitudinal direction in the direction in which the rotation shaft is directed, but it is also possible to be formed only in a partial section in the longitudinal direction.
  • the fluid applies pressure in a direction perpendicular to the plane in contact with the surface in contact with the fluid, and by the formation of this pressure intensifying groove 336, the pressure of the inflow fluid acts in a more efficient direction on the vane to increase the rotor rotation efficiency.
  • the pressure increasing/decreasing groove 336 may simply be a groove concave in the forward direction, but a part of the pressure increasing groove 336' forms a concave portion 336a' toward the center of the rotor, that is, in the direction of the rotation axis. As shown in the side view of Fig. 6, it can be installed so that an acute angle jaw is formed at the entrance of the groove.
  • the pressure of the inflow fluid acts on the concave portion 336a' of the pressure intensifying groove 336' to cause the vane 337 to enter the vane guide groove 331a inward, which is the first In the hole (355a), a high-pressure pressure fluid suddenly acts on the vane, pushing the vane forward, and at the same time, the vane 337 is in close contact with the inner wall surface of the casing to prevent rotational obstruction that prevents it from sliding naturally on the inner wall surface. have.
  • FIG. 6 A partial side view of FIG. 6 is shown in contrast to the two types of grooves formed in the vane as described above.
  • an elastic means such as a spring, that applies a restoring force to the outside (toward the inner wall of the casing) may be installed, and the elastic means is installed in the vane guide groove Or it can be installed around the hinge shaft.
  • this embodiment also shares a significant portion of the configuration with that of the first embodiment, and has basically the same shape in the combined configuration of the vane and the rotor body, so that the vanes basically perform the same operation. will lose
  • the rotor in addition to the configuration of the first embodiment above, the rotor is accommodated in the casing, and the pressure fluid injected through the pressure fluid inlet 455 of the casing is discharged through the pressure fluid outlet of the casing.
  • the end of the vane is made to be in contact with the inner wall surface while being held therein so that the position of the center of rotation within the casing is spaced apart from the rotation shaft 433, but further comprising a cylindrical inner cylinder 420 configured to rotate together when the rotor rotates, Accordingly, the pressure fluid inlet and outlet are installed in the closing plate (413, 415) portion to send the pressure fluid into the inner cylinder (420).
  • the casing encompasses the inner cylinder 420 and the rotor, and a cylindrical body 411a and this cylindrical body 411a that can secure a space in which the inner cylinder 420 can rotate.
  • the casing is made in the form of a cylindrical closed container having end plates 413 and 415 to close both ends, and at this time, the end plate portion is the longitudinal direction (rotation axis direction) of both ends of the inner cylinder, the rotor body 430 and the vane 435.
  • the pressure fluid can be installed to have a small gap that is difficult to leak, and the pressure fluid outlet and the pressure fluid inlet 455 are installed on both sides or one side of the finishing plate
  • the pressure fluid can be introduced into the partition space or flow out from the partition space when it overlaps with the partition space that is the inside of the cylindrical inner cylinder and the outside of the rotor body.
  • the vane 435 is connected to the hinge shaft 439 installed in a part of the rotor body 430 by a link rod 437 installed on one side of the vane (the front side when considering the rotation direction), and this link rod It is rotatably coupled to the rotor body 430 by a 437 and a hinge shaft 439 .
  • a link rod accommodating groove 431b is installed on the surface of the rotor body so that the link rod 437 can be accommodated therein.
  • a primary extension portion 431c is installed by partially removing the rotor body from the rear portion of the inlet of the vane guide groove 431a.
  • the rear entrance is partially removed from the inlet forming the vane guide groove at both ends in the longitudinal direction of the vane guide groove 431a formed in the rotor body 430 to form the primary extension portion 431c.
  • It further includes a secondary extension (431d) formed in a concave curved surface toward the rear surface of the finish plate and the vane through additional removal from both ends of the extension in the longitudinal direction of the rotor.
  • the secondary extension 431d is spatially connected to the primary extension 431c.
  • the secondary extension portion 431d forms a space that can more easily receive pressure fluid when the pressure fluid is injected through the pressure fluid inlet 455 formed in the closing plate, and extends the primary extension portion 431c to the rear to some extent. This allows the extension to overlap the pressure fluid inlet for a longer period of time during rotor rotation, allowing more fluid to enter.
  • the pressure fluid inlet 455 and the pressure fluid outlet installed on the finish plate overlap the space inside the casing body 411a and outside the rotor body 430, as well as the inner cylinder
  • the inner side of the 420 and the outer side of the rotor body 430 are positioned so as to overlap the separation space.
  • the pressure fluid inlet consists of a plurality, here three holes, and the plurality of holes and the pressure fluid outlet have an approximately constant width along a curve similar to an arc.
  • a plurality of holes constituting the pressure fluid inlet in each finish plate are arranged along a curved trajectory similar to the circumference of the finish plate. More precisely, when viewed from the side view, the secondary extension is arranged along the moving trajectory, and is limitedly installed in a position overlapping with a part of the primary extension and the secondary extension installed on the rotor body behind the vane. In this case, the pressure fluid passing through the holes enters the partition space between the rotor and the inner cylinder through these extensions and also limited by the rear surface of the vane.
  • the rotating rotor starts to communicate with the rearmost part of the arc-shaped first hole 455a at the back of the rearmost arc-shaped first hole 455a based on the rotational direction in the same phase as in FIG.
  • the front part of (455a) shows a state in which it is cut off from the secondary extension part (431d) of the front division space.
  • the second hole 455b and the third hole 455c are in a state just before being cut off after supplying the pressure fluid to the further front division space.
  • the pressure fluid flows into the divided space from the time when the extension forming the rearmost partitioned space and the rearmost first hole of the fluid inlet start to overlap with each other in the direction of rotation of the rotor to create a narrow space
  • the pressure fluid inflow continues while maintaining the overlap with the first hole.
  • the overlapping state with the first hole passes, the expanded portion of the divided space sequentially meets the second hole and the third hole to become an overlapping state, and more pressure fluid is supplied.
  • there are more holes constituting the fluid inlet so that the extension of the rotor can receive the pressure fluid from the more holes.
  • the first hole ( 455a) the fluid flowing in with strong pressure from the pressure fluid inlet enters from both ends in the longitudinal direction of the rotor and fills the entire partition space including the extension, and applies pressure while meeting the rear surface of the vane limiting the partition space.
  • the rotor As the rotor rotates with fluid pressure, it enters a section in which the inner wall surface of the rotor body 31 and the inner cylinder 20 is further widened, and the vane end is kept in contact with the inner wall surface of the inner cylinder 20 by centrifugal force while maintaining the vane guide groove ( 31a), the space between the inner cylinder and the rotor body 31 increases.
  • the fluid inlet is formed with three arc-shaped holes arranged along an arc-shaped curved trajectory corresponding to a central angle of about 90 degrees, and the time when the hole and the primary and secondary extensions of the rotor overlap during rotation of the rotor During only the inner cylinder 420 and the partition space between the rotor body 430 is connected to the fluid inlet, the pressure fluid is introduced.
  • the extension In the space between the inner cylinder and the rotor body 31, the extension first meets the fluid inlet at the position where the gap between the rotor body 31 and the inner cylinder begins, and in this part, the gap (space) between the rotor body and the inner cylinder is very small. As the pressure fluid is injected, a high pressure state is maintained, so that rotational force can be efficiently transmitted even with a small amount of the pressure fluid.
  • the mutual positional relationship between the rotor body and the vanes and the reciprocating angular motion are basically the same as in the first embodiment, except that the vanes of the rotor are Instead of sliding on the inner wall of the fixed casing, here, the vane is in contact with the inner wall of the inner cylinder and the rotor rotates and the vane reciprocates angularly to enter and exit the guide groove. The difference is that they rotate together. In this case, since there is a difference between the effective circumference of the rotor and the circumference of the inner cylinder, the number of rotations between the rotor and the inner cylinder is generally different.
  • a concave pressure intensifying groove 436 for changing the thickness of the vane is also formed on the upper rear surface of the vane 435 .
  • the concave pressure intensifying groove 436 is concavely formed in the direction of the front surface of the vane over the entire length when the direction in which the rotation shaft 433 is directed is viewed in the longitudinal direction.
  • a part of the rotor body is removed from the entrance of the vane guide groove to form an extension while chamfering or rounding, but an embodiment without such an extension is also possible.
  • a pressure-increasing groove is formed on the upper side of the rear surface of the vane to increase the pressure fluid action efficiency, and the case where there are a plurality of pressure fluid inlets is described, but the vane is formed without such a pressure-increasing groove at all, It is also possible to use a single inlet for the pressure fluid.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Hydraulic Motors (AREA)

Abstract

Est divulgué un moteur à ailettes comprenant : un boîtier ayant une entrée de fluide sous pression et une sortie de fluide sous pression, à travers laquelle un liquide sous pression est injecté ou évacué ; et un rotor qui est mis en rotation, à l'intérieur du boîtier, autour d'un arbre rotatif logé dans le boîtier, par la réception de la transmission de la pression du liquide sous pression, et qui a : un corps de rotor ayant une forme cylindrique dans son ensemble avec un axe central coïncidant avec l'arbre rotatif ; et des ailettes qui sont installées dans des rainures de guidage d'ailette formées dans le côté du corps de rotor et qui ont une largeur en saillie à partir des rainures de guidage d'ailette, la largeur variant en fonction de la phase de rotation, les ailettes ayant des formes d'arc lorsqu'elles sont vues depuis la direction de la longueur de l'arbre rotatif, les rainures de guidage d'ailette forment des rainures en forme d'arc pour recevoir les ailettes, et les ailettes sont reliées de manière rotative à une partie du corps de rotor par des tiges de liaison installées sur un côté des ailettes. Selon la présente invention, les ailettes sont formées en forme d'arc, et les ailettes en forme d'arc sont activées pour réaliser un mouvement de rotation selon la trajectoire d'arc, au lieu d'un mouvement de va-et-vient linéaire, et ainsi, des problèmes tels que le mauvais fonctionnement, l'usure et le frottement des ailettes peuvent être atténués.
PCT/KR2020/018807 2020-11-30 2020-12-21 Moteur à ailettes WO2022114366A1 (fr)

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JP2023532102A JP2023551252A (ja) 2020-11-30 2020-12-21 ベーンモーター
US18/200,758 US20230287792A1 (en) 2020-11-30 2023-05-23 Vane motor

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KR1020200164743A KR102428799B1 (ko) 2020-11-30 2020-11-30 베인 모터
KR10-2020-0164743 2020-11-30

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US18/200,758 Continuation US20230287792A1 (en) 2020-11-30 2023-05-23 Vane motor

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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3938478A (en) * 1974-04-29 1976-02-17 Piper Jack N Rotary internal combustion engine
JPH08144701A (ja) * 1994-11-18 1996-06-04 Uriyuu Seisaku Kk エアーモータ
JP2009047028A (ja) * 2007-08-16 2009-03-05 Mitaka Koki Co Ltd 蒸気駆動モータ
KR20090037376A (ko) * 2006-03-06 2009-04-15 네보자 보스코빅 고정형 및 회전형 실린더부를 갖는 베인머시인
KR20190093700A (ko) * 2014-11-28 2019-08-09 니토 코키 가부시키가이샤 베인식 에어 모터 및 베인식 에어 모터를 구비하는 에어 공구

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101199197B1 (ko) 2010-04-15 2012-11-07 신국선 베인 기구
KR101116511B1 (ko) 2011-10-05 2012-02-28 이병록 라이너가 구성된 에어베인모터
KR101874583B1 (ko) 2016-06-24 2018-07-04 김재호 베인모터

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3938478A (en) * 1974-04-29 1976-02-17 Piper Jack N Rotary internal combustion engine
JPH08144701A (ja) * 1994-11-18 1996-06-04 Uriyuu Seisaku Kk エアーモータ
KR20090037376A (ko) * 2006-03-06 2009-04-15 네보자 보스코빅 고정형 및 회전형 실린더부를 갖는 베인머시인
JP2009047028A (ja) * 2007-08-16 2009-03-05 Mitaka Koki Co Ltd 蒸気駆動モータ
KR20190093700A (ko) * 2014-11-28 2019-08-09 니토 코키 가부시키가이샤 베인식 에어 모터 및 베인식 에어 모터를 구비하는 에어 공구

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KR20220076008A (ko) 2022-06-08
KR102428799B1 (ko) 2022-08-04
US20230287792A1 (en) 2023-09-14
JP2023551252A (ja) 2023-12-07

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