Miniaturized vibration-free mechanical apparatus

Abstract

To provide a structure that enhances compactness in machinery, such as engines and pumps which combine low vibration of a Wankel-type rotary engine with high working-fluid sealing (high efficiency) of a piston engine, and engines employing a vibration-free mechanism layout referred to as an "enclosed radial rotor R-zero radial cylinder arrangement", which provides a vibration-free apparatus.SOLUTION: In machinery such as engines employing the vibration-free mechanism layout referred to as an "enclosed radial rotor R-zero radial cylinder arrangement," a cylinder 5 having a bore diameter that is four times or more an eccentric amount of a crank pin of a crankshaft is adopted, an ultra-short-stroke structure is set, a length of a radial line surface 1g of a radial rotor 1a that drives a thin piston is set to one half or less of the bore diameter of the cylinder 5, the cylinder 5 is shifted inward until the radial line surface 1g intrudes into an effective cylinder portion, and a special bearing is adopted, thereby further miniaturizing the radial rotor 1a.SELECTED DRAWING: Figure 1a

Description

[Technical Field]

[0001] The present invention relates to a miniaturized vibration-free mechanical device. [Background technology]

[0002] For example, reciprocating piston engines with crankshafts, pistons, and connecting rods vibrate and it is difficult to eliminate high-order vibrations, but piston rings provide excellent sealing. On the other hand, Wankel rotary engines are vibration-free, but fluid sealing is difficult and they are less efficient.

[0003] Patent Document 1 provides the principles and theoretical analysis of the "base radial mechanism," a highly efficient reciprocating piston type mechanism that does not require connecting rods and is vibration-free like a Wankel rotary engine. It describes that if the "number of elements n," which corresponds to the number of cylinders, is 2 or more, the total center of gravity position remains unchanged and vibration-free operation is possible, and if n is 3 or more, the total kinetic energy remains constant when rotating at a constant angular velocity, allowing for smooth operation.

[0004] Non-patent literature 1 and non-patent literature 2 published the mechanism described in patent literature 1.

[0005] The "base radial mechanism" will be explained below based on Patent Document 1.

[0006] As examples, firstly, examples relating to a two-axis fixed type are given as the seventh embodiment (Fig. 5 of Patent Document 1), the eighth embodiment (Fig. 6 of Patent Document 1), the ninth embodiment (Fig. 7 of Patent Document 1), and the tenth embodiment (Fig. 8 of Patent Document 1).

[0007] Next, Figure 9 of Patent Document 1 shows and explains the geometric configuration of the "fixed baseline radial shaft eccentric rotation type: shaft arrangement rotation type B." When realizing Figure 9 of Patent Document 1 in an actual machine, it was devised to perform circumferential movement of the "radial line rotating shaft" using a "crankshaft" or the like with an eccentricity amount d with the rotating shaft as the origin. In this case, it is described that in order to prevent vibration, a "static counterweight" and a "dynamic counterweight" should be installed on the axis of the "crankshaft."

[0008] In the base radial mechanism, the circular movement of this "radial line rotating axis" means the "non-rotating circular revolution" of the "radial rotor."

[0009] As an eleventh embodiment of this type, Patent Document 1 shows a design drawing of a prototype in Figure 10 and a photograph of the prototype in Figure 11. Patent Document 1 also describes, together with in-cylinder pressure fluctuation data in Figure 12, that this prototype succeeded in achieving "sustained operation," in which rotation is maintained solely by the action of fuel combustion.

[0010] The following explanation is given regarding the design parameters of this prototype:

[0011] The shaft arrangement rotation type is "baseline fixed radial shaft eccentric rotation type: shaft arrangement rotation type B" and the sealing method is "sealed method B".

[0012] The main angle synchronization method adopted is "Main angle synchronization method D" (see Figure 7 of Patent Document 1), which uses two normal-length "radial arms" and one "extended radial arm." The tip of the "extended radial arm" is driven by a "sub-crankshaft," which is an "orbital unit planar drive parallel crank" driven by a "synchronous gear train."

[0013] The number of orbital units n is n = 3, n = 3, d = 15 mm, R = 55 mm, f = 0, h = -10 mm, -30 mm, cylinder bore diameter 30 mm, stroke 30 mm, displacement 21 cc / cylinder, and compression ratio 4.9.

[0014] A rotary valve is used to supply and discharge the working fluid, and the "rotary valve gear" attached to the valve rotor, which is inserted and rotated at the tip of the "cylinder installed on the base plate," is driven by a "multiple-row scroll groove plate," which is rotated by the "main crankshaft." As a result, the "rotary valve" rotates once for every two rotations of the "main crankshaft," achieving a combustion cycle based on the Otto cycle.

[0015] Regarding vibration caused by the eccentric rotation of the mass of the extension part of the "extension radial arm," by designing the extension part so that its center of gravity is located on the crank pin axis of the "sub crankshaft," the "static counterweight" and "dynamic counterweight" on the "sub crankshaft" side can cancel out and prevent vibration.

[0016] The above is the description of the prototype design parameters.

[0017] Now, in FIG. 13 of Patent Document 1, the actual configuration in which the baseline radial line segment length R is set to R=0 and the "radial rotor" is strengthened is shown as the sixth example (twelfth embodiment) of design variations.

[0018] In the present invention, "Radial rotor" with high strength, with the baseline radius line length R set to R=0" "Radial line surrounded radial rotor" or "surrounded radial rotor" Let's call it this.

[0019] In addition, using a "radial line surrounding type radial rotor", "the actual machine configuration with the baseline radius line length R = 0" "Encircled Radial Rotor R Zero Radial Configuration" or "Encircled radial rotor R-zero radial cylinder arrangement" Let us call it this.

[0020] In the sixth example (twelfth embodiment) of the design variation of Patent Document 1, The shaft arrangement rotation type is "baseline fixed radial shaft eccentric rotation type: shaft arrangement rotation type B" and the sealing method is "sealed method B". "Main angle synchronization method E" was adopted as the "main angle synchronization method." Here, "Main Angle Synchronization Method E" is a method in which the "orbital unit planar synchronization arm" connected to the "radial rotor" and the "base plate" are linked together with one or more "orbital unit planar driving parallel cranks" on the "orbital unit plane," which is the plane on which the orbital unit exists.

[0021] In addition, FIG. 14 of Patent Document 1 also shows, as a seventh example (thirteenth embodiment), The configuration of "encircled radial rotor R-zero radial cylinder arrangement" is shown, but the only difference is that another "main angle synchronization method" is adopted. [Prior art documents] [Patent documents]

[0022] [Patent Document 1] "Vibration-free mechanism layout and its application equipment" Patent application No. 2022-101280 (filed June 23, 2022), Patent application No. 2024-002213 (published January 11, 2024) [Non-patent literature]

[0023] [Non-Patent Document 1] Proceedings of the 32nd General Symposium on Environmental Engineering 2022, Japan Society of Mechanical Engineers, "Prototype Study of a New Type of Vibration-Free Piston Engine Based on a Base-Radial Mechanism," Takuma Oikawa, Momoka Yoneda, Yojiro Ishino, July 7, 2022. [Non-patent document 2] Proceedings of the 33rd Internal Combustion Engine Symposium of the Japan Society of Mechanical Engineers, "Vibration-free internal combustion piston engine based on a base-radial mechanism (design and manufacture of a prototype engine and understanding of its actual operating characteristics)," Yojiro Ishino, Takuma Oikawa, Momoka Yoneda, Ryosuke Hibi, November 21, 2022. Summary of the Invention [Problem to be solved by the invention]

[0024] Regarding the engine (fluid machinery, machine) with the "surrounding radial rotor R-zero radial cylinder arrangement" shown in Figures 13 and 14 of Patent Document 1, the issues ((1) to (3)) that need to be resolved are listed below, and an explanation of each is provided.

[0025] Issue (1): Improving compactness Issue (2): Improve combustion pressure resistance Challenge (3): Simultaneous improvement of the crankshaft's strength, low friction, and ease of assembly

[0026] First, we will discuss the issue (1) of "compactness."

[0027] The engine with the "encircled radial rotor R-zero radial cylinder arrangement" shown in Figures 13 and 14 of Patent Document 1 has a small operating space (reference numeral 52 in Patent Document 1) compared to the size of the entire aircraft, making it less compact.

[0028] In other words, the amount of fuel burned and heat generated per crankshaft revolution is extremely small compared to current reciprocating engines and Wankel-type rotary engines, making it difficult to obtain practical output. To replace current engines, it is necessary to reduce the overall volume of the aircraft relative to the working space volume, and improve the engine structure to be "highly compact." (The reasons for this will be described in the solution.)

[0029] Next, regarding issue (2) "combustion pressure resistance," it is necessary to transmit large forces such as combustion pressure between the "piston-like raceway unit (reference number 6a in Patent Document 1)" and the "radial line (reference number 4 in Patent Document 1) (radial line surface)" of the "radial rotor (reference number 43 in Patent Document 1)" while allowing the two to slide laterally. However, in the structure described in Patent Document 1, the "radial line raceway unit bearing (reference number 6c in Patent Document 1)" inserted between the two is supported by a shaft from the "piston-like raceway unit (reference number 6a in Patent Document 1)," which has low support strength for the shaft, and it is not possible to use a large bearing; the low resistance of the tiny steel balls and needles inside the bearing reduces the resistance of the bearing itself.

[0030] Patent document 1 describes the use of "rollers" in this area, but does not mention their size. Furthermore, while the use of ordinary "rollers" can lead to misalignment, causing vibrations and other problems, there is no mention of how to control their position.

[0031] Regarding issue (3) "strength and ease of assembly of the crankshaft," the specific examples in Patent Document 1 all use "a crank rod supported at one end by a single crank pin."

[0032] The "crank rod supported at one end by a single crank pin" allows the insertion and connection of an object (mainly a "radial rotor (reference number 43 in Patent Document 1)") that is rotationally connected to the crank pin, and also makes it easy to insert a normal bearing between the two to minimize frictional resistance.

[0033] Although it may appear to be easy to assemble, because it is a "crank rod supported at one end," there are concerns about insufficient strength and reduced precision as a crank rod.

[0034] Figure 10 of Patent Document 1 shows an example of "support at both ends," but it is an "assembled crankshaft," and there is no denying that it is inferior in terms of precision and strength. [Means for solving the problem]

[0035] The present invention, which solves the above problems, is as follows.

[0036] The problem to be solved is an engine (fluid machinery, machine) with an "encircled radial rotor R-zero radial cylinder arrangement" shown in FIGS. 13 and 14 of Patent Document 1.

[0037] In engines, fluid machinery or machines with "surrounded radial rotor R-zero radial cylinder arrangement", "Body structure of quasi-octagonal and quasi-2n-gonal three-dimensional frame structure" "An enclosed radial rotor that moves non-rotatingly and circularly by three parallel cranks" "Multiple rollers that roll between the back surface of the thin piston and the radial line surface" "A thin piston having a rack gear on its back surface and a plurality of geared rollers that roll reliably between the radial line surface having a rack gear" "A sliding connection device between a piston and an enclosed radial rotor, in which the piston slides without separating from the radial rotor" "A radial rotor having a radial line surface that penetrates the effective portion of the cylinder and has a length that is shorter than half the diameter of the cylinder bore." "Crank with an eccentricity of less than one-quarter of the cylinder bore diameter" "A piston whose combustion chamber-facing part has been replaced with a low-heat-loss material," "A radial rotor having a crank hole through which a crankshaft passes" and It is characterized by being equipped with a "split needle bearing" An engine, fluid machine, or machine with an "encircled radial rotor R-zero radial cylinder arrangement."

[0038] "Encircled type radial rotor R zero radial cylinder arrangement" engine, fluid machinery or machinery, "body structure of quasi-octagonal quasi-2n polygonal three-dimensional frame structure", "An enclosed radial rotor that moves non-rotatingly and circularly by three parallel cranks" "Multiple rollers that roll between the back surface of the thin piston and the radial line surface" "A thin piston having a rack gear on its back surface and a plurality of geared rollers that roll reliably between the radial line surface having a rack gear" "A sliding connection device between a piston and an enclosed radial rotor, in which the piston slides without separating from the radial rotor" "A radial rotor having a radial line surface that penetrates the effective portion of the cylinder and has a length that is shorter than half the diameter of the cylinder bore." "Crank with an eccentricity of less than one-quarter of the cylinder bore diameter" "A piston whose combustion chamber-facing part has been replaced with a low-heat-loss material," "A radial rotor having a crank hole through which a crankshaft passes" and Among "split needle bearings", characterized by comprising at least one or more of: An engine, fluid machine, or machine with an "encircled radial rotor R-zero radial cylinder arrangement."

[0039] A device with a "quasi-octagonal and quasi-2n-gonal three-dimensional frame structure."

[0040] "An enclosed radial rotor that moves in a non-rotating circular orbital motion using three parallel cranks."

[0041] The piston has a rack gear on its rear surface and a plurality of geared rollers that roll reliably between the rack gear and the radial line surface. "A sliding connection device between a piston and an enclosed radial rotor, in which the piston slides without separating from the radial rotor."

[0042] A radial rotor that revolves around a circle without rotation due to a crank with an eccentricity of less than one-fourth of the cylinder bore diameter, and has a radial line surface that penetrates the active part of the cylinder and is shorter than half the cylinder bore diameter.

[0043] "A piston in which the part facing the combustion chamber has been replaced with a low-heat-loss material."

[0044] A machine having a crank hole through which a crankshaft passes, and a crank pin of the crankshaft is rotatably connected to the crank hole by a "split needle bearing." [Effects of the Invention]

[0045] The improvements made by this invention, using a vibration-free mechanism layout, enable vibration-free engines, pumps, etc. to be made smaller and with higher output, combining the low vibration characteristics of a Wankel rotary engine with the high working fluid sealing performance (high efficiency) of a piston engine. [Brief explanation of the drawings]

[0046] [Figure 1a] 1 is a front cross-sectional view showing the structure of a three-cylinder engine improved by the present invention (the piston of the upper cylinder is at the top dead center position). FIG. [Figure 1b] 1 is a diagram showing the side cross-sectional structure of a three-cylinder engine improved by the present invention (the piston of the upper cylinder is at the top dead center position). FIG. [Figure 1c] FIG. 1 is a diagram showing a detailed side cross-sectional structure of a piston driving sliding portion with a radial surface in a three-cylinder engine improved according to the present invention. [Figure 2a] 1 is a front cross-sectional view showing the structure of a three-cylinder engine improved by the present invention (the piston position of the upper cylinder is in the middle position; the radial rotor is at the rightmost position; also called the right middle position). [Figure 2b] 1 is an operational diagram showing a side cross-sectional structure of a three-cylinder engine improved by the present invention (the piston position of the upper cylinder is in the middle position; the radial rotor is at the rightmost position; also called the right middle position). [Figure 3a] 1 is a front cross-sectional view showing the structure of a three-cylinder engine improved by the present invention (the piston of the upper cylinder is at the bottom dead center position). FIG. [Figure 3b] 1 is a diagram showing the side cross-sectional structure of a three-cylinder engine improved by the present invention (the piston position of the upper cylinder is at bottom dead center). FIG. [Figure 4] This is a photo of the shape of the engine body without any accessories. [Figure 5] This photograph shows the body's three-dimensional shape, a "quasi-octagonal / quasi-hexagonal three-dimensional frame structure," and the presence of two secondary crankshafts. [Figure 6] This is a photograph showing the "quasi-octagonal and quasi-hexagonal three-dimensional frame structure." [Figure 7] This is a photograph showing the production of a "quasi-octagonal and quasi-hexagonal three-dimensional frame structure" using a hexagonal prism-shaped jig. [Figure 8] This is a photograph showing the pistons with the cylinder head of the upper cylinder removed from the prototype engine in the state shown in Figure 4. [Figure 9] This photo was taken from directly above the prototype engine in the state shown in Figure 8, with the piston removed. [Figure 10] This photograph was taken from the prototype engine in the state shown in Figure 9, with the upper cylinder removed and each crankpin moved upward, and then taken from a horizontal direction. [Figure 11] FIG. 2 is an explanatory diagram relating to design conditions of a geared roller. [Figure 12] This is a photograph of the actual part in the state shown in Figure 11(a) taken from the side. [Figure 13] This is a photograph of the actual part in the state shown in Figure 11(a) taken from diagonally above. [Figure 14] This is a photograph of the actual part in the state shown in Figure 11(b). [Figure 15] This is a photograph showing the structure of the back side of the piston, the geared roller, and the radial line surface. [Figure 16] FIG. 10 is a diagram showing a structure in which part of the combustion chamber surface of the piston is made of a material with low heat loss characteristics to reduce heat loss. [Figure 17] This is a photograph showing a split needle bearing in use. [Figure 18] This is a photo showing the structure of a split needle bearing with it partially removed. [Figure 19] This is a photograph showing the structure of a split needle bearing. [Figure 20]1 is a photograph showing a crankshaft body and a radial rotor having a crank hole that can pass through it. [Figure 21] 1 is a photograph showing a crankshaft body and a radial rotor having a crank hole that can pass through it. [Figure 22] 1 is a photograph showing a crankshaft body and a radial rotor having a crank hole that can pass through it. [Figure 23] FIG. 1 is a diagram showing a comparison of the size of a prototype engine of the present invention with a commercially available engine of equivalent displacement. DETAILED DESCRIPTION OF THE INVENTION

[0047] Hereinafter, embodiments of the present invention will be described with reference to the drawings. The present invention is not limited to the following embodiments, and changes, modifications, and improvements can be made without departing from the scope of the invention.

[0048] The present invention, which solves the above problems, is as follows.

[0049] The problem to be solved is an engine (fluid machinery, machine) with an "encircled radial rotor R-zero radial cylinder arrangement" shown in FIGS. 13 and 14 of Patent Document 1.

[0050] The issues that needed to be resolved were the above-mentioned issues (1) to (3).

[0051] 1a, 1b, 1c, 2a, 2b, 3a and 3b show the cross-sectional structure and operation of a three-cylinder engine incorporating the present invention (Embodiment 1: prototype engine).

[0052] FIG. 1a is an operational diagram showing the front cross-sectional structure of a three-cylinder engine improved by the present invention (the position of the "piston 2a" of the upper cylinder is the top dead center position). FIG. 1b is an operational diagram showing the side cross-sectional structure of a three-cylinder engine improved according to the present invention (the position of the "piston 2a" of the upper cylinder is the top dead center position). FIG. 1c is a diagram showing a detailed side cross-sectional structure of a piston driving sliding portion with a "radial surface 1g" in a three-cylinder engine improved according to the present invention.

[0053] FIG. 2a is an operational diagram showing the front cross-sectional structure of a three-cylinder engine improved by the present invention (the piston position of the upper cylinder is in the middle position: the "radial rotor 1a" is at the rightmost position: also called the right middle position). FIG. 2b is an operational diagram showing the side cross-sectional structure of a three-cylinder engine improved by the present invention (the piston position of the upper cylinder is in the middle position: the "radial rotor 1a" is at the rightmost position: also called the right middle position).

[0054] FIG. 3a is an operational diagram showing the front cross-sectional structure of a three-cylinder engine improved by the present invention (the position of the "piston 2a" of the upper cylinder is the bottom dead center position). FIG. 3b is an operational diagram showing the side cross-sectional structure of a three-cylinder engine improved according to the present invention (the position of the "piston 2a" of the upper cylinder is the bottom dead center position).

[0055] In Figures 1a, 2a and 3a, the upper cylinder of the three cylinders is referred to as the "upper cylinder", the lower right cylinder as the "right cylinder", and the lower left cylinder as the "left cylinder".

[0056] Figures 1b, 2b and 3b are cross-sectional views of Figures 1a, 2a and 3a seen from the side, respectively, and are designed so that the positions of the "upper cylinder," "radial rotor," "main crankshaft," and "auxiliary crankshaft (one of two)" can be seen.

[0057] Regarding part numbers, although major part numbers are described in Figures 2a, 2b, 3a and 3b, please refer to Figures 1a, 1b and 1c for details.

[0058] The engine of the first embodiment is designed with three orbital units. The number of orbital units may be 3 or more. Here, since three-cylinder engines are preferred and widely produced among current small engines, the example of the three-cylinder engine in embodiment 1 is also appropriate from a practical standpoint.

[0059] In embodiment 1, vibration-free piston drive is realized with a gasoline engine in mind, but it can also be applied to other types of engines, fluid machinery such as pumps, and vibration-free machines in which part of the orbital unit is a mechanical component.

[0060] The explanation of the "three-cylinder prototype engine incorporating the present invention" of the first embodiment will be continued.

[0061] Figure 4 shows a photograph of the engine body without accessories, with the "cylinder head 4" removed from the right and left cylinders.

[0062] The shaft protruding from the "semi-regular hexagon" (a hexagon with each vertex at 120°, with two or less different side lengths, and with alternating long and short sides; regular hexagons are also included) "body side plate 7c" on the front side is the output shaft of the "main crank body 8."

[0063] The photograph in Figure 5 shows the state of Figure 4 with all of the "cylinders 5" removed, and also with the "body side plate 7c (displayed on the floor)" removed, revealing the distinctive three-dimensional shape of the "body 7," a "quasi-octagonal / quasi-hexagonal three-dimensional frame structure," and the presence of two "sub-crankshaft bodies 9."

[0064] The "body side plate 7c" has the function of passing through and holding one "main crankshaft 8" in rotation, and non-passing and holding two "auxiliary crankshafts" in rotation, and fits into the quasi-hexagonal opening of the "body 7".

[0065] The "body 7" is made up of three "cylinder flange mounting body plates 7a," which are semi-octagonal plates that pass through the "cylinder barrel 5a" and screw the "cylinder flange 5b" to, welded together, minimizing the volume "below (towards the center)" of the "cylinder flange 5b."

[0066] Furthermore, three "body reinforcement parts 7b" are welded to connect the vertices of the semi-regular octagon for reinforcement and to form openings, and the "body 7" is completed.

[0067] This "quasi-octagonal / quasi-hexagonal three-dimensional frame structure" (Fig. 6; when the number of cylinders is n, it becomes a "quasi-octagonal / quasi-2n-gonal three-dimensional frame structure"), which contributes to the compactness of engines and other equipment, is a three-dimensional structure that is normally difficult to manufacture. However, by using a hexagonal prism-shaped jig during manufacturing, as shown in Fig. 7, it is possible to manufacture it by welding, etc., without the need for "machining," which is wasteful of time and material, making it easy to make it larger.

[0068] FIG. 8 is a photograph in which the "cylinder head portion 4 (displayed on the floor)" of the upper cylinder has been removed from FIG. 4, and the "piston 2a" of the upper cylinder can be seen.

[0069] Figure 9 is a photograph taken from directly above the upper cylinder with the "piston 2a (displayed on the floor)" removed, and shows the "radial rotor compression direction braking part (sliding plate) 1b" of the "encircled radial rotor 1" that drives (reciprocates) the backside of the "piston 2a," as well as the side of the "radial rotor 1a" and the "radial rotor side rack gear 1c." (The "radial rotor separation direction braking part (flange bearing) 1d" has been removed.)

[0070] It can also be seen that the "main crank pin 8a" and the "secondary crank pin 9a" penetrate into the "radial rotor main crank hole 1e" and the "radial rotor secondary crank hole 1f" of the "encircled type radial rotor 1", respectively.

[0071] The "encircled radial rotor 1" is forced to undergo "non-rotating circular revolution" by three parallel cranks, the "main crankshaft 8" and the "sub-crankshaft 9" (two cranks), which have the same eccentricity. (The realization of this motion by three parallel cranks has been confirmed on an actual machine.)

[0072] Furthermore, Figure 10 is a photograph taken from a horizontal direction after removing the upper cylinder "cylinder 5" from the state of Figure 9 and moving each crank pin upward. In this photograph, the "radial rotor side rack gear 1c" and "radial line (radial line surface) 1g" that drive the "piston 2a" protrude upward from the "cylinder flange mounting body plate 7a." In this mechanism, it can be seen that the cylinder has been moved toward the center so much that the "radial line surface 1g" penetrates into the interior of the "cylinder barrel 5a," achieving a compact design.

[0073] As shown in Figures 1a, 1b and 1c, the structure of the part where the "radial line surface 1g" of the "encircled radial rotor 1" drives the "piston 2a" is such that two or more "rollers 3" with a diameter (8 mm in the prototype engine) that satisfies the conditions described below are inserted between the back surface of the "piston 2a" and the "radial line surface 1g" of the "encircled radial rotor 1", minimizing lateral friction on the driving plane when the piston is driven.

[0074] In this machine, which uses a "base-radial mechanism," the "orbital unit (piston 2a)" is guided by the "cylinder inner wall 5a" so that the "piston 2a" moves back and forth along the "base line," thereby achieving this movement.

[0075] Therefore, it is desirable to reduce the contact pressure of the "piston 2a" against the "cylinder inner wall 5a", and to achieve this, it is desirable to have a mechanism that minimizes the sliding resistance between the "back surface of the piston 2a" and the "radial line surface 1g".

[0076] Now, analysis has confirmed that even with a roller having a large mass, if it is always in contact with both sides and rolls without slipping, the total center of gravity will move in a circular motion, making it easy to eliminate vibrations with a counterweight, and the total momentum will remain constant.

[0077] Therefore, two rows of "race unit side rack gears 2c" were installed on the "back surface of piston 2a," and two rows of "radial rotor side rack gears 1c" were installed on the "radial line surface 1g," and gears were installed on both ends of "roller 3" to form "geared roller 3," and by meshing these together, "roller 3" does not slip and always achieves its intended movement.

[0078] Furthermore, because large forces such as combustion pressure are applied to "Roller 3," if a direct force is applied to the meshing part of the gears, not only will smooth operation be impossible, but the gears may also be damaged.

[0079] Normally, there is a demand for using light materials for oscillating parts such as the "piston 2a" and the "radial rotor 1a," but light materials tend to have low strength.

[0080] Therefore, a "compression direction braking part (sliding plate) 2b on the raceway unit side" made of tool steel is attached to the back surface of the "piston 2a," and a "compression direction braking part (sliding plate) 1b on the radial rotor side" made of tool steel is also installed on the "radial line surface 1g."

[0081] In addition, "Roller 3" was made from high-hardness shaft steel.

[0082] The size and installation position of "Roller 3" or "Geared Roller 3" were designed to satisfy the following conditions.

[0083] FIG. 11 shows an explanatory diagram of the "geared roller 3."

[0084] The dimensions in Figure 11 are the dimensions of each part of the manufactured engine, and are shown as a good design example.

[0085] FIG. 11(a), which is the upper part of FIG. 11, is an explanatory diagram of the case where the lateral position of the "encircled type radial rotor 1" is located at the center of the cylinder.

[0086] 12 and 13 show photographs of the actual part in the state shown in FIG. 11(a).

[0087] In this state, it is assumed that force is applied to the central axis of the "piston 2a," so two or more "geared rollers 3" must be installed, with the two at both ends straddling the central axis. (The following describes the case where there are two rollers.)

[0088] Furthermore, the gears must not be in contact with each other, including at their tips (the gear with module 1 is placed on a roller with a diameter of 8 mm, with a spacing of 14.14 mm).

[0089] Next, FIG. 11(b), which is the lower part of FIG. 11, shows the case where the lateral position of the "encircled type radial rotor 1" has moved to the farthest right.

[0090] Figure 14 shows a photograph of the actual part in the state shown in Figure 11(b).

[0091] Because a cylinder with an inner diameter of 60 mm and a crank with an eccentricity of 13 mm were used, the "geared roller 3" moved 6.5 mm to the right and the "encircled radial rotor 1" moved 13 mm to the right.

[0092] At this time, if a clearance of 0.5 mm is provided to prevent the "radial surface 1g" of the "encircled-type radial rotor 1" from colliding with the "cylinder inner wall 5a," the length of the "radial surface 1g" will be 33 mm, and the left side of the "radial surface 1g" will be positioned to the left of the central axis. Furthermore, the "geared roller 3" on the left side that has moved must be placed on the "radial surface 1g" while also being to the left of the central axis (0.57 mm to the left in Figure 11(b)).

[0093] As a design condition for the "geared roller 3," it is desirable to use "rollers" with as large a diameter as possible in order to increase the strength of the contact surface of the "rollers."

[0094] The above are the conditions to be satisfied when a pressing force is applied to the center of the piston. However, it is also necessary to prepare for the case where a pressing force is applied other than the center or a tensile force is applied during the intake stroke or the like. For this purpose, a "track unit side separation direction braking part (sliding plate) 2d" is installed on the back surface of the "piston 2a", and a "radial rotor side separation direction braking part (flange bearing) 1d" is installed on the "radial line surface 1g" of the "surrounding type radial rotor 1", which are engaged with each other to prevent the inclination and separation of the "piston 2a".

[0095] Fig. 15 shows a structural photograph of the back side of the piston, the "roller 3 with gear" and the "radial line surface 1g" of the "surrounding type radial rotor 1".

[0096] Now, from the above description, when the "radial line surface 1g" is inserted into the "cylinder 5a" to achieve compactification, a relationship of e < D / 4 is found between the inner diameter D of the "cylinder 5a" and the eccentricity e of the "crankshaft" (the piston stroke amount S is S = 2e).

[0097] This means an engine structure with an extremely short stroke where S < D / 2, that is, the SD ratio defined by (piston stroke amount / cylinder bore diameter) is less than 0.5.

[0098] At this SD ratio, in the current engines using connecting rods, the connecting rods become too inclined and are unrealistic, so they have not been considered so far.

[0099] Therefore, in Patent Document 1, no idea for an extremely short stroke structure can be found, and the width of the "radial surface" of the "radial rotor" is longer than the inner diameter of the cylinder (bore diameter), and the "radial surface" cannot enter the "cylinder". Also, a piston with a thickness corresponding to the stroke amount is required, and the cylinder moves away in the outer peripheral direction, resulting in a large engine size.

[0100] In this invention, we have identified the advantages of a "base radial mechanism" that does not use a connecting rod, devised an extremely short stroke structure, and by making the length of the "radial surface" less than half the bore diameter, we have been able to make the "radial surface" penetrate into the "effective part of the cylinder," and also make it possible to use an "extremely thin piston" (for example, Figure 12), successfully moving the cylinder closer to the center.

[0101] The "short stroke engine" proposed in the present invention tends to have a large amount of heat loss to the combustion chamber wall surface and is therefore inefficient.

[0102] Therefore, as shown in Figure 16, a structure can be adopted in which part or all of the combustion chamber surface of the piston is replaced with a component that has lower heat loss characteristics than ordinary aluminum, such as a heat-resistant glass plate, quartz glass plate, or ceramic plate, to reduce heat loss. In other words, a "combustion chamber surface low heat loss material replacement structure" can be adopted.

[0103] To prevent damage to the part (for example, the "low heat loss material disc 14") due to thermal expansion, etc., it may be attached to the piston using a piston ring-like elastic material ("piston ring-like elastic material retainer part 15").

[0104] In order to minimize frictional resistance, needle bearings and rollers 3 are used on both ends of the crank, the back surface of the piston, the drive surface, etc., in addition to the sliding contact between the piston ring and the inner wall of the cylinder.

[0105] In particular, the rotational connection between the "main crank pin 8a" and "auxiliary crank pin 9a" and the "radial rotor main crank hole 1e" and "radial rotor auxiliary crank hole 1f" would normally require the use of a "split journal bearing" with high rotational sliding resistance and the division of the "radial rotor 1a," which would result in the "radial rotor 1a" becoming larger.

[0106] Alternatively, even if the crankshaft body is made into an assembly type, improving assembly ease and making it possible to make the "radial rotor 1a" non-divisible and use a normal bearing in that area, this would result in a decrease in the strength of the crankshaft body.

[0107] Therefore, in this invention, when installing three parallel cranks on the radial rotor 1a, we developed and used the split needle bearing 10a (Figs. 17, 18 and 19). This makes it possible to use a high-strength non-assembled crankshaft body.

[0108] The outer rings of the "split needle bearing 10a" (the two outer rings in Figure 19) may not be necessary if the material of the "radial rotor 1a" is hard enough, but they are necessary if a lightweight material is used.

[0109] The inner ring of the "split needle bearing 10a" was not used because the crank pin material was very hard, but it is expected that there may be cases where it is necessary.

[0110] For the split section of the inner and outer rings of the "split needle bearing 10a," if an interlocking structure is created with concave and convex portions as shown in the photograph (Figure 19), stability can be achieved during installation while preventing the rolling elements (needles) from becoming stuck.

[0111] Regarding the split section of the inner and outer rings of the "split needle bearing 10a," if one of the concave and convex end faces is concave and the other is convex and convex, as shown in the photograph (both sides of Figure 19), it is easy to manufacture a high-precision part. From a cost perspective, it is better to combine one type of concave and convex structure.

[0112] Next, regarding miniaturization by making the "radial rotor 1a" non-dividable, by focusing on the radial thickness of the "split needle bearing 10a" and designing a "radial rotor crank hole" large enough to allow the "crank shaft" to pass through as shown in Figures 20, 21 and 22, and filling the gap with a "split needle bearing," it is possible to retrofit needle bearings to the completed crank and simultaneously make the radial rotor non-dividable.

[0113] FIG. 23 shows a comparison of the size of a prototype engine of the present invention (displacement 220 cc) and a commercially available engine of the same displacement (200 cc) (main parts are shown shaded).

[0114] Compared to the comparison engine (main parts shown in gray), this unit (160 mm long x 165 mm wide x 125 mm deep) shown in black has been made compact to a fraction of its size.

[0115] Patent Document 1 gives an example of realizing "non-rotating circular revolution motion" of a radial rotor using one or two parallel cranks with gears that transmit driving force, but this has the potential for wear or chipping of the teeth of the drive gears. Therefore, this invention realizes "non-rotating circular revolution motion" of a radial rotor using three parallel cranks that do not require gears, and is characterized by increasing the durability of the mechanism that generates this motion. Output can be extracted from one or more crankshafts. Gears may be used to synchronize the rotation of the cranks in case of an emergency. [Industrial Applicability]

[0116] Regarding internal combustion engines, external combustion engines, or pumps that use a compact "vibration-free mechanism layout" ("base radial mechanism"), the internal combustion engines and external combustion engines can be used as NH3-fueled EV range extenders or H2 city gas cogeneration power generation internal combustion engines, while the pumps can be used for rocket propellants, artificial heart-lung machines, or pumps for quiet environments. This technology can be applied to mechanisms that are unsuitable for vibration generation and increases and decreases in kinetic energy, such as precision machinery like mechanical watches and mechatronic equipment in manufacturing plants, where multiple units rotate while in operation. [Explanation of symbols]

[0117] 1 "Radial Line Surrounded Radial Rotor" ("Surrounded Radial Rotor") 1a "Radial rotor" 1b "Radial rotor side compression direction braking part (sliding plate)" 1c "Radial rotor side rack gear" 1d "Radial rotor side separation direction braking part (flange bearing)" 1e "Radial rotor main crank hole" 1F "Radial rotor secondary crank hole" 1g "Radial line (radial line surface)" 2 "Orbital Unit" 2a "Piston" 2b "Railway unit side compression direction braking part (sliding plate)" 2c "Rack gear on track unit side" 2d "Track unit side separation direction braking part (sliding plate)" 3. "Geared roller" 4. Cylinder head 4a "Inner rotary valve mechanism" 4b "Visualization window" 4c "ignition electrode" 4d "Valve drive pulley" 4e "Intake and Exhaust Port Duct" 4f "Valve drive timing belt" 5 "Cylinder" 5a "Cylinder barrel" 5b "Cylinder flange" 6 "Compression ratio change shim (ring plate)" 7 "Body" 7a "Cylinder flange mounting body plate" 7b "Body reinforcement" 7c "Body side plate (crank bearing holder)" 8 "Main crankshaft body" 8a "Main crank pin" 8b "Main crank rotating shaft" 8c "Main crank web" 9 "Sub crankshaft body" 9a "Sub crank pin" 9b "Sub crank rotating shaft" 9c "Sub crank web" 10 "Crank pin rotating tool" 10a "Split needle bearing" 11 "Counterweight" 12. "Reverse rotation speed-increasing flywheel" 13 "Working Space" 14 “Low heat loss material disc” 15. "Piston ring-like elastic material retainer parts"

Claims

1. In engines, fluid machinery or machines with "surrounded radial rotor R-zero radial cylinder arrangement", "Body structure of quasi-octagonal and quasi-2n-gonal three-dimensional frame structure" "An enclosed radial rotor that moves non-rotatingly and circularly by three parallel cranks" "Multiple rollers that roll between the back surface of the thin piston and the radial line surface" "A thin piston having a rack gear on its back surface and a plurality of geared rollers that roll reliably between the radial line surface having a rack gear" "A sliding connection device between a piston and an enclosed radial rotor, in which the piston slides without separating from the radial rotor" "A radial rotor having a radial line surface that penetrates the effective portion of the cylinder and has a length that is shorter than half the diameter of the cylinder bore." "A crank with an eccentricity of less than one-fourth of the cylinder bore diameter" "A piston whose combustion chamber-facing part has been replaced with a low-heat-loss material," "A radial rotor having a crank hole through which a crankshaft passes" and It is characterized by being equipped with a "split needle bearing" An engine, fluid machine, or machine with an "encircled radial rotor R-zero radial cylinder arrangement."

2. In engines, fluid machinery or machinery with an "encircled radial rotor R-zero radial cylinder arrangement," "a body structure with a quasi-octagonal or quasi-2n-gonal three-dimensional frame structure"; "An enclosed radial rotor that moves non-rotatingly and circularly by three parallel cranks" "Multiple rollers that roll between the back surface of the thin piston and the radial line surface" "A thin piston having a rack gear on its back surface and a plurality of geared rollers that roll reliably between the radial line surface having a rack gear" "A sliding connection device between a piston and an enclosed radial rotor, in which the piston slides without separating from the radial rotor" "A radial rotor having a radial line surface that penetrates the effective portion of the cylinder and has a length that is shorter than half the diameter of the cylinder bore." "A crank with an eccentricity of less than one-fourth of the cylinder bore diameter" "A piston whose combustion chamber-facing part has been replaced with a low-heat-loss material," "A radial rotor having a crank hole through which a crankshaft passes" and Among "split needle bearings", It is characterized by having at least one or more of: An engine, fluid machine, or machine with an "encircled radial rotor R-zero radial cylinder arrangement."

3. "Quasi-octagonal and quasi-2n-gonal three-dimensional frame structure"

4. "An enclosed radial rotor with non-rotating circular revolution using three parallel cranks"

5. The piston has a rack gear on its rear surface and a plurality of geared rollers that roll reliably between the rack gear and the radial line surface. "A sliding connection device between a piston and an enclosed radial rotor, where the piston slides without separating from the radial rotor."

6. A radial rotor that revolves around a circle without rotation by "a crank with an eccentricity of less than one-fourth of the cylinder bore diameter" and "has a radial line surface that penetrates the effective part of the cylinder and is shorter than half the cylinder bore diameter."

7. "A piston whose combustion chamber-facing part has been replaced with a low-heat-loss material"

8. A machine having a crank hole through which a crankshaft passes, and a crank pin of the crankshaft is rotatably connected to the crank hole by a "split needle bearing."

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