JP2011202519A - Rotary cylinder device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a rotary cylinder device facilitating noise-reduction by reducing vibration accompanying rotation of piston sets installed to a piston complex eccentrically coupled to a first crankshaft rotating around a shaft and linearly reciprocating, and by reducing noise when taking in and exhausting fluid.SOLUTION: When the first crankshaft 308 rotates around the shaft 304, the piston complex P rotates around the first crankshaft 308 and thereby the plurality of piston sets 301, 302 linearly reciprocate along diametral directions of rolling circles 323 of a radius 2r of second virtual crankshafts 314a, 314b around the shaft 304, operation is performed for taking fluid into one of cylinder chambers 342 formed on opposite sides of the respective piston sets 301, 302 from an intake port 321f and for exhausting fluid from the other of the cylinder chamber 342 through a discharge valve 340a.

Description

  The present invention is applicable to various types of devices such as a rotary cylinder device that can mutually convert the rotational motion of the shaft and the reciprocating motion of the piston in the cylinder, more specifically, an internal combustion engine, a compressor, a vacuum pump, a fluid rotary machine, and the like. The present invention relates to a possible rotary cylinder device.

  For example, a compressor is used as a compressor in the oxygen concentrator. By controlling the drive of the motor that composes the compressor to concentrate oxygen to 90% or more from the raw air, and supplying the patient with concentrated oxygen from the nasal cannula, it is used to treat patients with respiratory diseases such as chronic bronchitis. (Patent Document 1).

  As a compressor used in the oxygen concentrator, a swing type pump that swings a piston mainly by driving a motor is used. For example, FIG. 13 shows an intake / exhaust structure of a compressor using a swing piston. A piston set 403 is connected to a crankshaft 402 connected to the shaft 401 via a crank arm (not shown) with a predetermined eccentricity. An annular seal cup 404 is integrally assembled with a piston head portion 403 a provided on the front end side of the piston assembly 403 by a seal cup retainer 405. The piston head part 403 a is inserted into the cylinder 406. A first cylinder head 407 and a second cylinder head 408 are assembled to the opening end of the cylinder 406.

  A cylinder chamber 409 is formed between the first cylinder head 407 and the piston head portion 403a, and an intake chamber 410a and an exhaust chamber 410b are formed between the first cylinder head 407 and the second cylinder head 408, respectively. Has been. The first cylinder head 407 includes an intake valve (intake valve) 407 a for connecting and closing the intake chamber 410 a with respect to the cylinder chamber 409 and an exhaust valve (exhaust valve) 407 b for opening and closing the exhaust chamber 410 b with respect to the cylinder chamber 409. Is provided. The second cylinder head 408 is provided with an intake port 408a that intakes air into the intake chamber 410a and an exhaust port 408b that exhausts air from the exhaust chamber 410b. The intake valve 407a and the exhaust valve 407b are respectively provided on the opposite surfaces of the first cylinder head 407, and are urged so as to always close the first cylinder head 407 by, for example, a leaf spring.

  When the shaft 401 is rotated by operating the drive source, the crankshaft 402 rotates, and the piston set 403 linked to the crankshaft 402 reciprocates while swinging. 14 (a) to 14 (e), the piston set 403 performs intake from the top dead center (a) to the intake chamber 410a and the cylinder chamber 409, moves to the bottom dead center, the intake ends, and the cylinder chamber 409 is compressed. FIG. 8 is an explanatory diagram showing a process of exhausting to the exhaust port 408b through the exhaust chamber 410b, and ending exhaust when the piston set 403 reaches top dead center.

JP 2002-45424 A

Since the intake chamber 410a and the exhaust chamber 410b are separately formed between the first cylinder head 407 and the second cylinder head 408, the first cylinder head 407 is provided with an intake valve 407a and an exhaust valve 407b. ing. For this reason, in addition to the vibration caused by the reciprocating motion of the swinging piston assembly 403, the fluid sound when passing through the valve with the flow path restricted, the impact sound and vibration sound due to the opening and closing of the valve, etc. And on the exhaust side. For this reason, the cause of noise generation increases, and it is necessary to strengthen anti-vibration measures and sound-proof measures, resulting in a complicated and large device structure.
In addition, since the piston assembly 403 swings together with the reciprocating motion, the range in which the piston body linearly moves is short. Therefore, a sufficient fluid flow rate is ensured unless the cylinder diameter is increased or the length of the piston body is increased. This makes it difficult to increase the size of the apparatus.

  An object of the present invention is to reduce vibrations associated with rotation of a piston assembly that is assembled in a piston complex that is eccentrically connected to a first crankshaft that rotates about a shaft, and to perform intake and exhaust of the piston assembly that reciprocates linearly. An object of the present invention is to provide a rotary cylinder device that reduces noise and promotes quietness.

In order to achieve the above object, the present invention has the following configuration.
A rotary cylinder device capable of mutually converting rotational movements of a piston and a shaft that reciprocate in a cylinder, and is assembled eccentrically with respect to the shaft center of the shaft, and has a radius r around the shaft. A first crankshaft rotatably assembled via a virtual crank arm, a first cylinder fitted concentrically to the first crankshaft, and an eccentricity with respect to the axis of the first cylinder The first cylinder is provided with an eccentric cylindrical body in which a second cylindrical body having a plurality of second virtual crankshafts as axial centers is continuously formed, and a plurality of piston sets intersect with each other in the second cylindrical body. A piston complex rotatably fitted through a second virtual crank arm having a radius r around the shaft, and both ends of the first crankshaft into which the piston complex is fitted; Times in the center First and second balance weights that balance the rotation between rotating parts, and the first crankshaft and the first and second balance weights that support the shaft rotatably and rotate around the shaft, A main body case that rotatably accommodates the piston complex that rotates about the first crankshaft, and a piston head portion that is slidably inserted into the main body case, and an intake port on a sliding surface of the cylinder And a cylinder head that is assembled so as to close the cylinder opening so as to face the piston head portion inserted into the cylinder and has only a discharge valve that forms a cylinder chamber. The first crankshaft rotates about the shaft, and the piston complex rotates about the first crankshaft. One cylinder formed at both ends of each piston set when a plurality of piston sets perform linear reciprocating motion along the radial direction of the rolling circle of radius 2r of the second virtual crankshaft centered on the shaft An intake operation is performed to the chamber from the intake port, and an exhaust operation is alternately performed from the other cylinder chamber through the discharge valve.

  Here, the first virtual crank arm is a portion that connects between the shaft and the axis of the first crankshaft, and a component that can be recognized as having a crank arm even if the crank arm does not exist as a single component. To tell. The second virtual crank arm is a portion that connects the shaft centers of the first crank shaft and the second virtual crank shaft, and the existence of the crank arm on the mechanism is recognized even if the crank arm is omitted. To tell. The second virtual crankshaft is a crankshaft in which the existence of an axis serving as the center of rotation is virtually recognized even if no crankshaft is present on the mechanism. Further, the piston assembly means that a seal member such as a seal cup, a seal cup pressing member, and a piston ring is integrally assembled to a piston head portion of a single piston.

  Further, a through hole or a groove hole connected to the intake port is formed on a sliding surface on which a piston head portion of the cylinder slides.

  Further, the edge portion facing the sliding surface of the through hole or the groove hole is formed with a relief portion including any of an R surface, a chamfered portion, and a tapered surface.

  When the rotary cylinder device according to the present invention is used, when the plurality of piston sets perform linear reciprocating motion along the radial direction of the rolling circle having the radius 2r of the second virtual crankshaft centered on the shaft, The vibration due to reciprocating motion can be suppressed and noise can be reduced, and by omitting the intake valve from the cylinder head, fluid noise when passing through the intake valve, impact sound and vibration noise due to opening and closing of the valve are reduced. Silencing can be promoted. Further, since the intake valve normally provided in the cylinder head can be omitted, the number of parts can be reduced and the shape of the cylinder head can be easily formed.

Also, if the through hole or groove hole connected to the intake port is formed in the sliding surface on which the piston head part of the cylinder slides, the number of parts is reduced, and the intake and intake air can be made with a simple structure by the reciprocating motion of the piston head part. A valve can be formed.
Even if a through hole or a slot is provided in the cylinder body, the stroke of the piston assembly can achieve a stroke (4r) that is four times the eccentric amount r of the first crankshaft with respect to the shaft. A sufficient intake / exhaust operation can be performed without increasing the size.

  Further, when an escape portion including any one of an R surface, a chamfered portion, and a tapered surface is formed on the edge portion facing the sliding surface on which the piston head portion of the through hole or the groove hole slides, It is possible to prevent biting or breakage of the seal cup provided on the piston head portion that slides on the sliding surface.

It is a perspective view of the rotary type cylinder device which removed the 1st and 2nd cylinder head. FIG. 2 is an axial sectional perspective view of the rotary cylinder device of FIG. 1. It is a disassembled perspective view of a rotary cylinder apparatus. It is a model principle figure which shows the relationship between the rotational motion of the 1st crankshaft centering on a shaft and a 2nd virtual crankshaft, and the reciprocating motion of several crank arms. It is a disassembled perspective view of the rotary cylinder apparatus which assembled | attached the 1st, 2nd cylinder head. It is a schematic diagram which shows the structure where the 1st cylinder head and the 2nd cylinder head were assembled | attached to the cylinder. It is the perspective view which shows the form of the cylinder trunk | drum of FIG. 6, a top view, and arrow AA direction sectional drawing. It is a disassembled perspective view of the rotary cylinder apparatus which assembled | attached the 1st, 2nd cylinder head which concerns on another example. FIG. 9 is a perspective view, a plan view, and a cross-sectional view in the direction of arrow EE showing the form of the cylinder body of FIG. 8. It is the perspective view which shows the other form of the cylinder trunk | drum of FIG. 9, a top view, and arrow EE direction sectional drawing. It is operation | movement explanatory drawing which shows the linear reciprocation of a 1st, 2nd piston group. It is explanatory drawing which shows the linear reciprocating motion and intake / exhaust operation | movement of a 1st, 2nd piston group. It is a schematic diagram of the compressor using a rocking piston set. It is explanatory drawing which shows the linear reciprocating motion and intake / exhaust operation | movement of a rocking | swiveling piston group.

An embodiment for carrying out the invention will be described in detail with reference to the accompanying drawings.
A rotary cylinder device will be described with reference to FIGS. In the rotary cylinder device, the rotary motion of the shaft (drive shaft) 304 is converted into the linear reciprocating motion of the first and second piston sets 301 and 302 and output.

  In FIG. 1, a shaft 304 (drive shaft) is rotatably supported by a main body case 307 constituted by a first main body case 305 and a second main body case 306. The shaft 304 is assembled and connected to an output shaft of an electric motor (not shown). The first main body case 305 and the second main body case 306 are assembled together by screwing four corners with bolts 307a.

  In the main body case 307, as shown in FIG. 2, an eccentric cylindrical body 303 rotatable around the first crankshaft 308, and a first piston set 301 and a second piston assembly assembled to the eccentric cylindrical body 303 are provided. A piston set 302 (hereinafter referred to as “piston complex P”) is rotatably accommodated. This will be specifically described below.

  In FIG. 2, the first crankshaft 308 is eccentrically connected to the axis of the shaft 304. In the present embodiment, the shaft 304 is formed integrally with the first balance weight 309. A shaft may also be formed on the second balance weight 310 side. The first and second balance weights 309 and 310 are fitted into the shaft end portions of the first crankshaft 308 and assembled together.

  In FIG. 3, slits 308 a are formed in the axial direction at both shaft ends of the first crankshaft 308. A pin hole 308b is provided in a part of each slit 308a. The hole diameter of the pin hole 308b is formed larger than the width of the slit 308a.

  In FIG. 2, first and second balance weights 309 and 310 are integrally assembled to both ends of the first crankshaft 308 by bolts 312a and 312b. The shaft 304 integrally formed with the first balance weight 309 is rotatably supported by the first bearing 313a, and the shaft portion 310c formed on the second balance weight 310 is rotatably supported by the second bearing 313b. Has been. The first and second balance weights 309 and 310 have, for example, a fan-shaped block shape and are assembled so as to be rotatable around the shaft 304. The first and second balance weights 309 and 310 balance the mass of the rotational motion around the shaft 304 including the first crankshaft 308 and the piston complex P, and particularly the first and second piston sets 301 and 302. It is provided to reduce the influence of the eccentric center of gravity generated by the linear reciprocation.

  2 includes a plurality of second virtual crankshafts 314a and 314b (see FIG. 4A) that are eccentric with respect to the axis of the first crankshaft 308. In the present embodiment, since there are two intersecting pistons, the second virtual crankshafts 314a and 314b are provided at positions that are 180 degrees out of phase with the first crankshaft 308 as the center.

  As shown in FIG. 2, the first and second pistons 301 and 302 intersect with each other and are assembled to an eccentric cylindrical body 303 that rotates about the first crankshaft 308. Specifically, the eccentric cylindrical body 303 includes a first cylindrical body 303a through which the first crankshaft 308 serving as a rotation center is inserted, and a second cylindrical body 303b that is continuous with the first cylindrical body 303a. Each is formed continuously on both sides. A first crankshaft 308 is fitted concentrically into the first cylinder 303 a and serves as the center of rotation of the eccentric cylinder 303. Further, the axis of the second cylinder 6b coincides with the second virtual crankshafts 314a and 314b that are eccentric with respect to the axis of the first crankshaft 5 (see FIG. 4A). . The first and second piston sets 301 and 302 are rotatably fitted to the second cylindrical body 303b provided on both axial sides through outer bearings 316a and 316b.

  Further, as shown in FIG. 2, inner bearings 315a and 315b are held on the inner peripheral side of the second cylinder 303b, and outer bearings 316a and 316b are held on the outer peripheral side. The inner bearings 315a and 315b support the first crankshaft 308 in a rotatable manner. The outer bearings 316a and 316b are fitted so that the first and second piston sets 301 and 302 intersect the second cylinder 303b so as to intersect each other in the direction perpendicular to the axis and rotate.

  As described above, the first and second piston groups 301 and 302 are assembled so that the pistons intersect (orthogonally) and overlap the second cylinder 303b of the eccentric cylinder 303. The piston head portions 301c and 302c are assembled so as to be able to reciprocate on the same plane. Therefore, the piston complex P (see FIG. 2) can be assembled in the height direction and the radial direction in a compact manner, and space-saving can be achieved in a small size and weight.

  Further, as shown in FIG. 3, the first piston head portion 301c and the second piston head portion 302c provided at both longitudinal ends of the first and second piston sets 301 and 302 include ring-shaped seal cups 317a, 317b and seal cup pressing members 318a and 318b are assembled by bolts 319, respectively. For the seal cups 317a and 317b, an oil-free seal material (for example, PEEK (polyether ether ketone) resin material or the like) is used. Upright portions 317c are erected on the outer peripheral edge portions of the seal cups 317a and 317b in the piston sliding direction. In a compressor, a fluid rotating machine, or the like, the upright portion 317c is assembled toward the outside in the sliding direction of the first and second piston head portions 301c and 302c.

  In FIG. 2, a cylinder 321 is assembled with a bolt 322 in an opening provided on a side surface (four surfaces) of the main body case 307 (the first main body case 305 and the second main body case 306). The first and second piston groups 301 and 302 slide with seal cups 317a and 317b (see FIG. 3) while maintaining the sealing performance with the inner wall surface of the cylinder 321.

  The cylinder 321 is integrally assembled to the main body case 307 by inserting the cylinder body 321c into the opening of the main body case 307, overlapping the flange 321b on the side surface, and fitting the bolt 322 with the through hole and the bolt hole. (See FIG. 1).

  In FIG. 1, the flange portion 321b is provided with bolt holes 321e at a plurality of locations. This is because, as will be described later, when assembling first and second cylinder heads 340 and 341, which will be described later, overlaid on the cylinder 321, bolt holes for bolt fitting are required.

FIG. 3 shows an example of the assembly configuration of the rotary cylinder device.
The inner bearings 315a and 315b are assembled to the second cylinder 303b of the eccentric cylinder 303. Further, the first crankshaft 308 is fitted into the inner holes 315a and 315b of the eccentric cylindrical body 303 and the center hole of the first cylindrical body 303a (see FIG. 6). Further, the seal cups 317 a and 317 b and the seal cup pressing members 318 a and 318 b are integrally assembled to the first and second piston head portions 301 c and 302 c of the first and second pistons 301 and 302 with a bolt 319. Further, the outer bearings 316a and 316b are assembled so as to fit into the bearing holding portions of the first and second pistons 301 and 302, respectively. Then, the first and second pistons 301 and 302 are fitted into the second cylindrical portion 303b so as to intersect with each other via the outer bearings 316a and 316b.

  Also, the first and second balance weights 309 and 310 are fitted into both ends of the first crankshaft 308, the pins 311a and 311b are fitted into the pin holes 308b, and the bolts 312a and 312b are tightened to tighten the first and second balances. The weights 309 and 310 are assembled integrally with the end portion of the first crankshaft 308. Further, the first bearing 313 a is fitted into the bearing holding portion 305 a of the first main body case 305, and the second bearing 313 b is fitted into the bearing holding portion 302 a of the second main body case 302. Then, the first main body case 305 and the second main body case 306 are combined so that the shaft 304 is fitted into the first bearing 313a and the shaft portion 310c of the second balance weight 310 is fitted into the second bearing 313b. Thus, the eccentric cylindrical body 303 and the first and second pistons 301 and 302 (piston complex P) assembled so as to intersect with the eccentric cylindrical body 303 are accommodated in the main body case 307 (see FIG. 1). Then, with the bolt hole 305c and the bolt hole 306c aligned and superimposed, the main body case 307 is assembled by fitting the bolt 307a. Finally, the cylinder 321 is fitted into the opening formed on the side surface (four surfaces) of the main body case 307, and the first piston head portion 301c and the second piston head portion 302c slide in the opening 321a of the cylinder 321, respectively. It fits in (see FIG. 1).

  In FIG. 5, the first cylinder head 340 and the second cylinder head 341 are assembled on the end surface (flange portion 321b) of the cylinder 321 provided on the four surfaces so as to close the cylinder opening, and the rotary type The cylinder device is assembled. A cylinder 321 into which one of the first piston head portions 301c of the first piston set 301 is inserted, and a structure in which the first cylinder head 340 and the second cylinder head 341 are assembled to the end surface (flange portion 321b) of the cylinder 321. This is schematically shown in FIG.

  In FIG. 6, a cylinder chamber 342 is formed between the first cylinder head 340 and the first piston head portion 301c. Further, only the discharge valve 340a is formed in the first cylinder head 340. An exhaust chamber 343 is formed between the first cylinder head 340 and the second cylinder head 341, respectively. The second cylinder head 341 has a discharge port 341a. The cylinder body 321c into which the first piston head 301c is slidably inserted is formed with a plurality of intake ports 321f in a part of the sliding surface 321h. The intake port 321f is formed within a range in which the first piston set 301 reciprocates between the top dead center and the bottom dead center, and communicates with the cylinder chamber 342 when the first piston set 301 is at the bottom dead center. It has become.

  The form of the cylinder 321 will be specifically described. In FIGS. 7A to 7C, the air inlet 321f communicates with a through hole 321g formed in the cylinder body 321c. The through holes 321g are provided at a plurality of locations (for example, four locations) at equal intervals in the circumferential direction. It is preferable that an escape portion including any one of an R surface, a tapered surface, and a chamfered portion is formed at the edge portion facing the sliding surface 321h of the through hole 321g (see FIG. 7C). Note that the intake port 321f communicating with the through hole 321g may be formed only at one location in the cylinder body 321c.

  FIG. 8 shows another example of the rotary cylinder device. Although the schematic configuration of the cylinder device is the same as that of FIG. 5, the cylinder device shown in FIG. 8 has a groove 321i formed in the cylinder 321 along the axial direction in the sliding surface 321h in place of the through hole 321g. .

  The form of the cylinder 321 will be specifically described. In FIGS. 9A to 9C, the air inlet 321f communicates with a slot (square hole) 321i formed in the cylinder body 321c. The slots 321i are provided at a plurality of locations (for example, four locations) at equal intervals in the circumferential direction. It is preferable that an escape portion including any one of an R surface, a tapered surface, and a chamfered portion is formed at an edge portion facing the sliding surface 321h of the slot 321i (see FIG. 9C). Note that the intake port 321f communicating with the groove 321i may be formed only in one place in the cylinder body 321c.

As another form of the groove hole, as shown in FIGS. 10A to 10C, a tapered groove 321j is formed so that the groove depth gradually increases from the sliding surface 321h toward the cylinder end. May be.
When the shape of the edge portion facing the sliding surface 321h of the cylinder head 321 is gentle, the seal cups 317a and 317b (see FIG. 3) provided in the first and second piston head portions 301c and 302c are engaged. And can prevent damage.

The rotary cylinder device assembled as described above has a rotational balance (first balance) around the outer bearings 316a and 316b (second virtual crankshafts 314a and 314b) of the first and second piston sets 301 and 302, The rotation balance (second balance) around the first crankshaft 308 of the piston complex P and the rotation balance (third balance) of the components around the shaft 304 are adjusted and assembled by balance weights 309 and 310. Yes.
As a result, the first crankshaft 308 is rotated about the shaft 304, the eccentric cylinder 303 is rotated about the first crankshaft 308, and the piston complex P is generated by the linear reciprocating motion of the first and second piston sets 301, 302. Even if an eccentric center of gravity is generated, vibration due to rotation can be suppressed and noise reduction can be achieved, and mechanical loss can be reduced to increase energy conversion efficiency.

  Here, the schematic structure shown in FIGS. 4A to 4L shows the relationship between the rotational motion of the first crankshaft 308 and the second virtual crankshafts 314a and 314b around the shaft 304 and the reciprocating motion of the plurality of piston sets. This will be described with reference to the principle diagram. 4A to 4L, the center O of the rolling circle 323 coincides with the axis of the shaft 304. Further, it is assumed that the first crankshaft 308 exists at a position eccentric from the center O, and the second virtual crankshafts 314a and 314b rotate without slipping as the first crankshaft 308 rotates. The number of second virtual crankshafts 314a and 314b corresponds to the number of pistons.

  A center distance r between the shaft 304 (center O) and the first crankshaft 308 is defined as the arm length (rotation radius) of the first virtual crankarm and the second virtual crankarm. Further, the first crankshaft 308 rotates on the rotation track 330 around the axis (center O) of the shaft 304 with the arm length r of the first virtual crank arm as the rotation radius. Further, the second virtual crankshafts 314a and 314b rotate without apparently slipping on a rotation path (virtual circle 324) having an arm length r of the second virtual crankarm centered on the first crankshaft 308 as a rotation radius. To do. As a result, the first and second piston sets 301 and 302 reciprocate linearly around the center O along the radial direction (inner cycloid) of the rolling circle 323 having the radius R (2r) of the virtual circle 324 as the radius. It is like that.

  In the present embodiment, the second virtual crankshaft of the second cylinder 303b in which the first and second piston sets 301, 302 that are orthogonal to each other are linked is illustrated as 314a, 314b. 4A, the second virtual crankshaft 314a is at the intersection (lower end position) of the rolling circle 323 and the diameter R1, and the second virtual crankshaft 314b is the center O of the rolling circle 323 (the axial center position of the shaft 4). )It is in. The first crankshaft 308 is assumed to be located at a radius r from the center O of the rolling circle 323.

  A case where the first crankshaft 308 rotates once counterclockwise around the center O of the rolling circle 323 will be described. It is assumed that the virtual circle 324 rotates in the clockwise direction without rotating along the inner circumference of the circle 323. 4A to 4L show a state in which the first crankshaft 308 is displaced by 30 degrees.

  When the first crankshaft 308 is rotated 90 degrees counterclockwise from the position shown in FIG. 4A, the position becomes the position shown in FIG. At this time, the second virtual crankshaft 314a moves to the center O on the diameter R1 of the rolling circle 323, and the second virtual crankshaft 314b reaches the intersection (right end position) between the diameter R2 orthogonal to the diameter R1 and the rolling circle 323. Moving.

  When the first crankshaft 308 is further rotated 90 degrees counterclockwise from the position shown in FIG. 4D, the position shown in FIG. 4G is reached. At this time, the second virtual crankshaft 314a moves to the intersection (upper end position) between the rolling circle 323 and the diameter R1, and the second virtual crankshaft 314b moves to the center O of the rolling circle 323.

  When the first crankshaft 308 is further rotated 90 degrees counterclockwise from the position of FIG. 4G, the position of FIG. 4J is reached. At this time, the second virtual crankshaft 314a moves to the center O of the rolling circle 323, and the second virtual crankshaft 314b moves to the intersection (left end position) between the rolling circle 323 and the diameter R2.

  When the first crankshaft 308 is further rotated 90 degrees counterclockwise from the position shown in FIG. 4J, the position shown in FIG. 4A is obtained. At this time, the second virtual crankshaft 314a moves to the intersection (lower end position) between the rolling circle 323 and the diameter R1, and the second virtual crankshaft 314b moves to the center O of the rolling circle 323.

  As described above, when the first crankshaft 308 rotates around the center O (shaft 304), the second virtual crankshaft 314a moves on the diameter R1 of the rolling circle 323 that is the rolling locus (inner cycloid) of the virtual circle 324. The second virtual crankshaft 314b reciprocates on the diameter R2 of the rolling circle 323.

  That is, with the rotational movement of the first crankshaft 308 and the piston complex P (see FIG. 2) along the rotation path 330 having the radius r about the axis (center O) of the shaft 304, the second virtual crankshaft In the second cylindrical portion 303b having 314a and 314b as the axis, the first piston 301 linked to the eccentric cylindrical body 303 is on a diameter R1 of a rolling circle 323 having a radius 2r (a concentric circle centered on the axis of the shaft 304). The reciprocating motion is repeated, and the second piston 302 repeats the reciprocating motion on the diameter R2 of the rolling circle 323 having a radius of 2r (a concentric circle with the axis of the shaft 304 as the center).

  FIGS. 11A to 11E are operation explanatory views illustrating the intake and exhaust operations accompanying the change in the rotation angle of the shaft 4 in the rotary cylinder device. The rotation angle of the shaft 4 is described by being identified by the counterclockwise rotation position of the integrally formed first balance weight 309. Further, the description will focus on the state of the cylinder chamber 342 formed at the left end of the first piston set 301 among the cylinder chambers 342 formed at four locations by the two piston sets.

  11A shows that the first piston set 301 is at the top dead center position (origin position; the rotation angle of the first balance weight 309 is 0 °), and FIG. 11B shows that the first piston set 301 is moved from the top dead center position. FIG. 11C shows a state in which the first piston set 301 is moving toward the bottom dead center (the inside of the cylinder chamber 342 is vacuum). 11 (d) shows that when the first piston set 301 passes in the vicinity of the intake port 321f of the cylinder 321, the outside air is sucked into the intake port due to the pressure difference between the inside and outside of the cylinder chamber 342. FIG. 11 (e) shows a state where the gas is sucked instantaneously through 321f (the rotation angle of the first balance weight 309 is 135 °). FIG. Satisfaction It shows the state (the rotation angle 170 ° of the first balance weight 309). When the shaft 304 further rotates in the same direction, the first piston set 301 moves from the bottom dead center toward the top dead center, so that the process proceeds to a process of compressing and exhausting the outside air sucked into the cylinder chamber 342.

12A to 12E are schematic views illustrating the intake and exhaust operations until the first piston set 301 returns from the top dead center to the top dead center again through the bottom dead center.
The first piston set 301 performs the intake operation (FIG. 12B) from the top dead center (FIG. 12A), moves to the bottom dead center, and ends the intake (FIG. 12C).

  Next, when the first piston set 301 moves from the bottom dead center toward the top dead center, the air in the cylinder chamber 342 is compressed, the discharge valve 340a is opened, and the discharge port 341a passes through the exhaust chamber 343. A state in which the compressed air is exhausted is shown (FIG. 12D). When the first piston set 301 reaches the top dead center again (FIG. 12 (e)), the exhaust operation ends. Intake into the cylinder chamber 342 moves to the bottom dead center and the intake ends, the cylinder chamber 342 is compressed and exhausted to the discharge port 341a through the exhaust chamber 343, and the first piston set 304 is brought to the top dead center. It reaches and exhaust ends. Thereafter, the same operation is repeated, and the movement of the second piston set 302 is different, but the intake and exhaust operations are the same.

As described above, when the piston complex P is rotated around the shaft 304, vibration due to the reciprocating motion of each piston set can be suppressed, and the intake valve can be omitted from the cylinder head. Since the fluid sound when passing through the intake valve, the impact sound and vibration sound due to the opening and closing of the valve are reduced, the noise reduction can be promoted.
Further, since the intake valve normally provided in the cylinder head can be omitted, the number of parts can be reduced and the shape of the cylinder head can be easily formed.

  The above-described rotary cylinder device can be used for, for example, a compressor (compressor) of an oxygen concentrator, and is expected to be applied to various devices such as an internal combustion engine, a compressor, a vacuum pump, and a fluid rotating machine. .

P Piston complex 301 1st piston set 301c 1st piston head part 302 2nd piston set 302c 2nd piston head part 303 Eccentric cylindrical body 303a 1st cylindrical body 303b 2nd cylindrical body 304 Shaft 305 1st main body case 305a, 306a Bearing holding portion 305c, 306c, 309a, 310a, 318c, 321e Bolt hole 306 Second body case 307 Body case 307a, 312a, 312b, 319, 322 Bolt 304 Shaft 308 First crankshaft 308a Slit 308b Pin hole 309 First Balance weight 310 Second balance weight 310c Shaft 311a, 311b Pin 313a First bearing 313b Second bearing 314a, 314b Second virtual crankshaft 315a, 315b Inner bearing 316a, 31 b Outer bearing 317a, 317b Seal cup 317c Standing portion 318a, 318b Seal cup holding member 321 Cylinder 321a Opening 321b Flange 321c Cylinder body 321f Inlet 321g Through-hole 321h Sliding surface 323 Rolling circle 330 324 Cylinder 324 Rotating track 331 Output shaft 340 First cylinder head 340a Discharge valve 341 Second cylinder head 341a Discharge port 343 Exhaust chamber

Claims (3)

A rotary cylinder device capable of mutually converting the rotational motion of a piston and a shaft that reciprocate in a cylinder,
A first crankshaft assembled eccentrically with respect to the shaft axis of the shaft and rotatably assembled via a first virtual crank arm having a radius r around the shaft;
A first cylinder fitted concentrically to the first crankshaft and a second cylinder having a plurality of second virtual crankshafts eccentric to the axis of the first cylinder are continuous. And a plurality of piston sets intersecting with each other while being intersected with each other so as to be rotatable through a second virtual crank arm having a radius r. A piston complex,
First and second balance weights that are respectively assembled at both ends of the first crankshaft into which the piston complex is fitted, and that balances rotation between rotating parts around the shaft;
The shaft is rotatably supported, and the first crankshaft and the first and second balance weights that rotate about the shaft and the piston complex that rotates about the first crankshaft are rotatable. A main body case for housing;
A cylinder that is assembled to the main body case, the piston head portion is slidably inserted, and an intake port is formed on a sliding surface of the cylinder; and
A cylinder head formed only with a discharge valve which is assembled so as to close the cylinder opening facing the piston head portion inserted into the cylinder and forms a cylinder chamber;
The first crankshaft rotates about the shaft, and the piston complex rotates about the first crankshaft so that the plurality of piston sets center on the shaft. When performing a linear reciprocating motion along the radial direction of a rolling circle having a radius of 2r, an intake operation is performed from one intake port to one of the cylinder chambers formed at both ends of each piston set, and discharge is performed from the other cylinder chamber. A rotary cylinder device characterized in that exhaust operations are alternately performed through valves.   The rotary cylinder device according to claim 1, wherein a through hole or a groove hole connected to the intake port is formed on a sliding surface on which a piston head portion of the cylinder slides.   The rotary cylinder device according to claim 2, wherein an escape portion including any one of an R surface, a chamfered portion, and a tapered surface is formed at an edge portion facing the sliding surface of the through hole or the groove hole.

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