VALVE OPERATING SYSTEM OF INTERNAL COMBUSTION ENGINE

Abstract: A valve operating system of an internal combustion engine, comprising an engine valve (5) having a valve shaft portion (5a) and a valve body portion (5b) provided at a tip end of the valve shaft portion, said engine valve being supported on a body (1) of the engine for opening and closing operations while being resiliently biased in a valve-closing direction, and a driving member (12) for driving said engine valve in a valve-opening direction being operatively connected to a rear end of said valve shaft portion, wherein a sleeve (10) is fixed to the body of the engine and is provided with a bottomed sliding bore (10a) having at a bottom portion thereof a guide hole (10b) through which said valve shaft portion (5a) is air-tightly and movably passed, and wherein a piston (16) of a bottomed double cylindrical shape is fixed to a portion of the valve shaft portion (5a) close to the rear end thereof and is slidably fitted in said sliding bore (10a) through a seal member (14) with a closed end of the piston facing axially outwardly so as to form an air pressure chamber (13) between the piston (16) and the bottom portion of the sliding bore (10a).

Description: The field of the invention is a valve operating system of an internal combustion engine, comprising an engine valve having a valve shaft portion and a valve body portion provided at a tip end of the valve shaft portion, the engine valve being supported on a body of the engine for opening and closing operations while being resiliently biased in a valve-closing direction, and a driving member for driving the engine valve in a valve-opening direction being operatively connected to a rear end of the valve shaft portion. Valve operating systems of the above mentioned type are known, for example, from Japanese Patent Application Laid-open No. 36906/89. In such a conventional system, a valve spring is used for biasing the engine valve in a valve-closing direction, and the engine valve is driven in a valve-opening direction by the driving member against a spring force of the valve spring. However, in the conventional system using such a spring force, since there is a limit in the natural frequency of the valve spring, the operation of the engine valve corresponding to a high rotation of the engine may become difficult. Accordingly, another prior art in which an air spring is used for biasing the engine valve in the valve-closing direction has been realized as shown in Fig. 6. In this prior art, a bottomed cylindrical lifter 35 driven by a cam 40 is slidably fitted in a guide bore 36 provided in a body 1 of an engine and is abutted against a rear or stem end of a valve shaft portion 5a of an intake valve 5 or an exhaust valve. A piston 37 fixed to a halfway of the valve shaft portion 5a is slidably fitted in a sleeve 39 with a front surface of the piston 37 being exposed to an air pressure chamber 38. In this prior art, since the intake valve 5 or the exhaust valve is biased in the valve-closing direction by the air pressure of the air pressure chamber 38 and so the resonance limit inherent to the natural frequency need not be taken account of, it is possible to drive the engine at a higher speed. However, the piston 37 is formed in a flat plate shape, and in order to secure a stroke of the piston 37 accompanying the opening and closing operations of the intake valve 5 or the exhaust valve, it is necessary to make the axial length of the sleeve 39 relatively long. FR-A-2 537 207 shows a pneumatic biasing system of an inlet valve of an internal combustion engine wherein a bottomed cylindrical lifter is slidably fitted in a bore of the engine cylinder, the lifter being interposed between a cam and the rear end of the valve shaft. The present invention has been proposed in view of the above mentioned circumstances, and it is an object of the invention to provide a compact valve operating system of an internal combustion engine which may enable the engine to be operated at a high speed. From FR-A-2 529 616 it is known to provide a valve operating system of an internal combustion engine, comprising an engine valve having a valve shaft portion and a valve body portion provided at a tip end of the valve shaft portion, said engine valve being supported on a body of the engine for opening and closing operations while being resiliently biased in a valve-closing direction, and a driving member for driving said engine valve in a valve-opening direction being operatively connected to a rear end of said valve shaft portion, wherein a sleeve is fixed to the body of the engine and is provided with a bottomed sliding bore having at a bottom portion thereof a guide hole through which said valve shaft portion is air-tightly and movably passed, and wherein a piston, comprising an inner cylindrical portion connected by a closed end to an outer coaxial cylindrical portion, is fixed to a portion of the valve shaft portion close to the rear end thereof and is slidably fitted in said sliding bore through a seal member with the closed end of the piston facing axially outwardly so as to form an air pressure chamber between the piston and the bottom portion of the sliding bore. According to the present invention, said outer cylindrical portion of the piston is extended to a position lower than said inner cylindrical portion and a bottomed cylindrical lifter is slidably fitted in said sliding bore and is interposed between said driving member and the rear end of said valve shaft portion, said piston being inserted in said lifter, and a communication groove opening to the outside is formed at an inner surface of the sliding bore such that the communication groove is capable of communicating with a space between said lifter and said piston at a position on that side of the seal member which is close to the lifter. Owing to the above arrangement, since a part of the air pressure chamber is formed within the piston, the axial length of the sleeve can be shortened, contributing to a compactness in structure. A preferred embodiment of the invention will now be described with reference to the accompanying drawings, in which:- Figs. 1 to 3 illustrate a valve operating system not in accordance with the present invention but included herein to assist understanding of Figures 4 and 5 which show a preferred embodiment of the invention. In the drawings: Fig. 1 is a longitudinal sectional side view of a valve operating system. Fig 2 is an enlarged longitudinal sectional view of a valve shaft seal member; and Fig 3 is an enlarged view of a portion III in Fig. 1. Figs. 4 and 5 illustrate an embodiment of the present invention, wherein Fig. 4 is a longitudinal sectional side view of a valve operating system of the present invention; and Fig. 5 is a view seen in the direction of the line V - V of Fig. 4. Fig. 6 is a longitudinal sectional side view of a prior art. In Fig. 1, a body 1 of an engine is bored with an intake port 4 leading to an intake valve opening 3 which is disposed so as to be exposed to a ceiling surface of a combustion chamber 2. An intake valve 5 as an engine valve for opening and closing the intake valve opening 3 is vertically movably guided through a guide cylinder 6 which is provided in the body 1 of the engine. That is, the intake valve 5 comprises a valve shaft portion 5a which is slidably passed through the guide cylinder 6, and a valve body portion 5b which is capable of opening and closing the intake valve opening 3 and provided at a tip end of the valve shaft portion 5a. The valve shaft portion 5a is vertically driven. At an upper portion of the body 1 of the engine, a valve operating cam shaft 7 operatively connected to a crankshaft (not shown) is rotatably disposed around an axis perpendicular to a direction of the valve shaft portion 5a of the intake valve 5. The valve operating cam shaft 7 is integrally provided with a cam 8 comprising a circular base portion 8a corresponding to a valve-closing timing of the intake valve 5 and a lobe portion 8b corresponding to a valve-opening timing of the valve 5. A support shaft 9 having an axis parallel to the valve operating cam shaft 7 is fixedly disposed between the valve shaft portion 5a of the intake valve 5 and the cam shaft 7. And a rocker arm 12 as a driving member is interposed between the valve shaft portion 5a of the intake valve 5 and the cam 8, and an intermediate portion of the rocker arm 12 is swingably supported around the support shaft 9. One end portion of the rocker arm 12 slide contacts with the cam 8 from upward, and a bearing 11 for slide contacting with a rear end of the valve shaft portion 5a of the intake valve 5 is pivotally supported at the other end portion of the rocker arm 12. A sleeve 10 is fixed to the upper portion of the body 1 of the engine at a position corresponding to the intake valve 5. The sleeve 10 is bored with a bottomed sliding bore 10a which is opened upwardly and is coaxial with the valve shaft portion 5a, and the sliding bore 10a is provided at its bottom portion with a guide hole 10b through which that portion of the valve shaft portion 5a which is projected upwardly from the guide cylinder 6 is movably passed. Further, secured with a portion of the valve shaft portion 5a closer to the rear end thereof is a piston 16 which is slidably fitted in the sliding bore 10a via a seal member 14 made of elastic material while forming an air pressure chamber 13 between the piston 16 and the bottom portion of the sliding bore 10a. The piston 16 comprises an outer cylindrical portion 16a, an inner cylindrical portion 16b disposed coaxially with the outer cylindrical portion 16a and a connecting flat plate portion 16c connecting between one ends of the outer and inner cylindrical portion 16a and 16b, and is formed into a bottomed double cylindrical shape. The piston 16 is fitted in the sliding bore 10a with the connecting plate portion 16c being located axially outwardly. Furthermore, an annular groove 17 is provided in a portion of the outer cylindrical portion 16a closer to the other end thereof, i.e., in an outer surface of the piston 16 closer to an opening end thereof, and a seal member 14 is fitted in the annular groove 17. An annular engaging groove 18 is provided in a portion of the valve shaft portion 5a closer to its rear end, and the piston 16 is fixed to the portion of the valve shaft portion 5a closer to its rear end via a slit cotter double-cut 19 which is engaged with the engaging groove 18. In particular, the inner cylindrical portion 16b of the piston 16 is provided with a through hole 20 which is tapered toward the air pressure chamber 13, and an outer surface of the cotter 19 is also formed tapered toward the air pressure chamber 13. Thus, the piston 16 is coaxially fixed to the valve shaft portion 5a by pressing the cotter 19 which is engaged with the engaging groove 18 into the through hole 20 from upward. Meanwhile, in order to prevent air in the air pressure chamber 13 from leaking out from between the guide hole 10b and the valve shaft portion 5a as well as from the jointed surfaces of the body 1 of the engine and the sleeve 10, an O-ring 21 surrounding the guide cylinder 6 is interposed between the jointed surfaces of the body 1 of the engine and the sleeve 10. Further, in order to prevent air in the air pressure chamber 13 from leaking out from between the cotter 19 and an outer surface of the valve shaft portion 5a and between the cotter 19 and an inner surface of the through hole 20, a valve shaft seal member 22 is fitted to an inner end of the inner cylindrical portion 16b of the piston 16. As shown in Fig. 2, the seal member 22 is made of elastic material, and comprises a cylindrical portion 22a formed in a substantially cylindrical shape for allowing the valve shaft portion 5a to pass through the cylindrical portion 22a while tightly contacting with the outer surface of the valve shaft portion 5a, and a flange portion 22b integrally and radially projected from an end portion, of the cylindrical portion 22a, closer to the side of the air pressure chamber 13. Also, an outer peripheral surface of the cylindrical portion 22a is tapered toward the flange portion 22b so as to correspond to the through hole 20. In Fig. 3, the seal member 14 fitted in the annular groove 17 provided in an outer surface of the outer cylindrical portion 16a of the piston 16 is substantially formed in a U-shape in cross section opened to the air pressure chamber, and comprises a support portion 14a which is substantially formed in an L-shape in cross section and fitted in the annular groove 17, and a lip portion 14b which is connected at its small diameter end with the support portion 14a and is formed so as to become larger in diameter as heading downward so that the outermost periphery of the lip portion 14b slide contacts with the inner surface of the sliding bore 10a upon receipt of pressure in the air pressure chamber 13. Further, a pressurized air supply source 25 is connected to the air pressure chamber 13 through a duct line 24 having a check valve. 23. The check valve 23 is arranged so that it allows the air flow only from the pressurized air supply source 25 to the air pressure chamber 13 in response to the reduction of the air pressure in the air pressure chamber 13 to less than that in the pressurized air supply source 25 for more than a predetermined value. For example, the pressurized air of 5 kg/cm² is supplied from the pressurized air supply source 25, and the check valve 23 is opened when the pressure in the air pressure chamber 13 is reduced to 4 kg/cm² or less. Further, a relief valve 30 is connected to the air pressure chamber 13 through a relief passage 29 bored in the sleeve 10. The relief valve 30 is set to be opened at a valve opening pressure (e.g. 16 kg/cm²) which corresponds to the maximum pressure in the air pressure chamber 13 when a predetermined amount of the lubricant oil has gathered in the chamber 13. And the relief passage 29 is bored in the sleeve 10 at a position lower than an oil level ℓ of the lubricant oil which has gathered in the air pressure chamber 13 to the predetermined amount, but upper than the guide bore 10b, so as to be communicated to the air pressure chamber 13. The relief valve 30 is disposed in the sleeve 10 so as to be interposed between the relief passage 29 and the passage 31 which is bored in the sleeve 10 and opened to an outside surface of the sleeve 10. The relief valve 30 comprises a spherical valve body 32 capable of bringing into and out of the communication between the relief passage 29 and the passage 31, and a spring 33 for biasing the valve body 32 in a valve-closing direction. The sleeve 10 is provided at a central bottom portion thereof with a concave 34 surrounding a portion, of the valve shaft portion 5a, passing through the guide bore 10b and projected into the air pressure chamber 13. Next, the operation of this illustrated embodiment will be described hereinafter. When the valve operating cam 7 is driven for rotation by the crankshaft, the rocker arm 12 is swung by the slide contact of the one end portion of the arm 12 with the cam 8. When the one end portion of the arm 12 slide contacts with the lob portion 8b of the cam 8, the valve shaft portion 5a is pressed downwardly through the bearing 11 and the intake valve 5 is opened. At that time, the piston 16 fixed to the rear end portion of the valve shaft portion 5a is also pressed downwardly while compressing the volume of the air pressure chamber 13, and thereby the air pressure is generated in the chamber 13. This causes the intake valve 5 to be biased upwardly, i.e., in a valve-closing direction by the air pressure, and the cam 8 opens the intake valve 5 against the biasing force in the valve-closing direction by the air pressure. Therefore, when the cam 8 is rotated to a position where the circular base portion 8a slide contacts with the rocker arm 12, the piston 16 is raised by the air pressure in the air pressure chamber 13 so that the one end of the rocker arm 12 slide contacts with the circular base portion 8a, and the intake valve 5 is closed. By the arrangement where the intake valve 5 is biased in the valve-closing direction by the air pressure in the above described manner, since it is not necessary to take into account the resonance limit by the natural frequency, it is possible to drive the engine at a higher speed or revolution, as compared with the art where the intake valve is biased in the valve-closing direction by a valve spring. Further, by such a valve operating system, the rocker arm 12 presses the valve shaft portion 5a downwardly through the bearing 11, and the bearing 11 does not apply to the valve shaft portion 5a a force in a direction perpendicular to an axial direction thereof. Thus a force applied from the piston 16 to the sleeve 10 is suppressed in a low level, and thus, it is not necessary to set a strength of the sleeve 10 to a particulary large level. Also, since the piston 16 is formed in a bottomed double cylindrical shape, a part of the air pressure chamber 13 can be formed within the piston 16. Further, since the seal member 14 is fitted in the outer surface of the piston 16 closer. to the opening end thereof, the axial length of the sleeve 10 can be shortened while largely securing the volume of the air pressure chamber 13, contributing to a compactness in a whole structure. Further, the valve shaft seal member 22 is mounted to the through hole 20 of the piston 16 in such a manner that the cylindrical portion 22a which is substantially cylindrically formed so as to correspond to the through hole 20 is resiliently fitted into the inner end of the inner cylindrical portion 16b from the side of the air pressure chamber 13. Therefore, the connecting and disconnecting operation of the seal member 22 is easy. Moreover, since there is no need to provide a mounting portion having a special configuration at a side of the piston 16, the arrangement can be simplified, contributing to reductions of the weight and the number of machining steps. Also, the valve shaft seal member 22 exerts a resilient force in its mounted state to the piston 16, and can hold the piston 16 at the valve shaft portion 5a, the pressing operation of the cotter 19 into the through hole 20 becomes easy when assembling. Further, since the flange portion 22b is tightly contacted with the inner end of the inner cylinder portion 16b by the air pressure in the air pressure chamber 13, the valve shaft seal member 22 exerts a sufficient sealing effect. Meanwhile, since the seal member fitted in the outer surface of the piston 16 is substantially formed in a U-shaped in cross section opened toward the air pressure chamber 13, and the outermost periphery of the lip portion 14b is slide contacted with the inner surface of the sliding bore 10a, when the piston 16 is depressed, i.e., when the intake valve 5 is opened, the lip portion 14b is operated to scratch and remove the lubricant oil downwardly, and on the other hand, when the piston 16 raises, i.e., when the intake valve 5 is closed, the lip portion 14b is operated to get over the oil film adhering to the inner surface of the sliding bore 10a. Thus, the lubricant oil is smoothly supplied to the inner surface of the sliding bore 10a and the lubrication between the piston 16 and the inner surface of the sliding bore 10a is carried out excellently. When the lubricant oil which is to be supplied to the portion between the piston 16 and the inner surface of the sliding bore 10a is gathering within the oil pressure chamber 13, the maximum pressure in the air pressure chamber 13 raises at the time of the opening of the intake valve 5 at its maximum. Thus, when the amount of oil gathering in the air pressure chamber 13 exceeds the predetermined level, and the maximum pressure in the chamber 13 exceeds the valve opening pressure of the relief valve 30, the valve 30 is opened. At the time of the opening of the relief valve 30, since. the relief passage 29 is communicated to the interior of the air pressure chamber 13 at a position lower than the predetermined lubricant oil level ℓ , such lubricant oil is mainly emitted to outside through the relief passage 29, the relief valve 30 and the passage 31, and the useless emission of the air in the air pressure chamber 13 can be avoided. Further, since the relief passage 29 is communicated to the interior of the air pressure chamber 13 at a position higher than the guide hole 10b, and the concave portion 34 is provided at the central bottom portion of the sliding bore 10a at a position also higher than the guide bore 10b, the lubricant oil required for lubricating the portion between the valve shaft portion 5a and the inner surface of the guide hole 10b gathers in the concave portion 34, and the portion between the valve shaft portion 5a and the sleeve 10 can sufficiently be lubricated. Further, if the air in the air pressure chamber 13 is reduced by leakage or the like, the pressurized air is supplied to the air pressure chamber 13 from the pressurized air supply source 25 through the check valve 23, and hence, the minimum pressure within the air pressure chamber 13 can be maintained and the biasing force which is enough for reliably closing the intake valve 5 can be secured. Figs. 4 and 5 illustrate an embodiment of the present invention, wherein portions corresponding to those in the previous embodiment are designated by the same reference numerals and characters. A bottomed cylindrical lifter 26 as a driving number is slidably fitted in an upper portion of the sliding bore 10a of the sleeve 10 with a closed end of the lifter 26 being located outwardly, the cam 8 slide contacts with an outer surface of the closed end of the lifter 26, and the inner surface of the closed end of the lifter 26 abuts against the rear end of the valve shaft portion 5a of the intake valve 5. The piston 16 is secured with a portion, of the valve shaft portion 5a closer to its rear end, and is slidably fitted in the sliding bore 10a via the seal member 14. Also, the piston 16 is inserted into the lifter 26 while forming an air chamber 27 between the piston 16 and the lifter 26. Further, an outer diameter of an outer cylindrical portion 16a of the piston 16 is set such that a minute annulus or clearance is formed between the inner surface of the lifter 26. Further, the inner surface of the sliding bore 10a is provided with a communication groove 28 which is axially extended so that an upper end of the groove 28 is communicated with the outside. The location of a lower end of the communication groove 28 is set so that when the circular base portion 8a of the cam 8 is slide contacted with the lifter 26 and the intake valve is in its closing state, i.e., when the piston 16 is at its uppermost position,. the lower end of the communication groove 28 is located above the seal member 14 to be communicated to the air chamber 27 through the minute annulus between the lifter 26 and the piston 16. In this embodiment, the intake valve 5 depresses the piston 16 downwardly to be opened in response to the lifter 26 being pressed downwardly by the cam 8. Further, since in the sliding bore 10a of the sleeve 10 in which the piston 16 is fitted, the lifter 26 is also slidably fitted, there is no need to provide above the intake valve 5 an arrangement to guide the lifter 26, this structure together with the arrangement of the piston 16 formed into a bottomed double cylindrical shape can contribute to a compactness in a whole structure. Also, when the intake valve 5 is in its closed state, the air chamber 27 is communicated to the outside through the annulus between the lifter 26 and the piston 16 and the communication groove 28, and hence, it can prevent the pressure within the air chamber 27 from abnormally increasing to generate a bouncing and noise by a float or relief of the lifter 26. Further, it is also possible to release the air from the air chamber 27 when assembling the lifter 26, and at that time, a release of the piston 16 from the valve shaft portion 5a by an increase of the pressure in the air chamber 27 can be avoided, And when removing the lifter 26, the pressure in the air chamber 27 can be prevented from decreasing by introducing the air into the air chamber 27, and the removing operation becomes easy. By the way, the communication groove 28 also has a function to introduce a part of the lubricant oil which is supposed to be supplied to the sliding surfaces of the cam 8 and the lifter 26, into the sliding bore 10a as a lubricant oil between the piston 16 and the inner surface of the sliding bore 10a. Thus, the lip portion 14b of the seal member 14 fitted in the outer surface of the piston 16 downwardly scratches and removes the lubricant oil which is introduced from the communication groove 28 when the piston 16 is depressed, and the lip portion 14b gets over the oil film adhering to the inner surface of the sliding bore 10a when the piston 16 raises. Therefore, the lubricant oil is smoothly supplied from the communication groove 28 to the inner surface of the sliding bore 10a, and the lubrication between the piston 16 and the inner surface of the sliding hole 10a is carried out excellently. In the above embodiment, although the explanation has been made especially based on the intake valve 5 as an engine valve, the present invention is also applicable to the valve operating system of the exhaust valve.

Claims: A valve operating system of an internal combustion engine, comprising an engine valve (5) having a valve shaft portion (5a) and a valve body portion (5b) provided at a tip end of the valve shaft portion (5a), said engine valve (5) being supported on a body of the engine for opening and closing operations while being resiliently biased in a valve-closing direction, and a driving member (8) for driving said engine valve (5) in a valve-opening direction being operatively connected to a rear end of said valve shaft portion (5a), wherein a sleeve (10) is fixed to the body of the engine and is provided with a bottomed sliding bore (10a) having at a bottom portion thereof a guide hole (10b) through which said valve shaft portion (5a) is air-tightly and movably passed, and wherein a piston (16), comprising an inner cylindrical portion (16b) connected by a closed end (16c) to an outer coaxial cylindrical portion (16a), is fixed to a portion of the valve shaft portion (5a) close to the rear end thereof and is slidably fitted in said sliding bore (10a) through a seal member (14) with the closed end (16c) of the piston (16) facing axially outwardly so as to form an air pressure chamber (13) between the piston (16) and the bottom portion of the sliding bore (10a), characterised in that said outer cylindrical portion (16a) of the piston (16) is extended to a position lower than said inner cylindrical portion (16b) and in that a bottomed cylindrical lifter (26) is slidably fitted in said sliding bore (10a) and is interposed between said driving member (8) and the rear end of said valve shaft portion (5a), said piston (16) being inserted in said lifter (26), and a communication groove (28) opening to the outside being formed at an inner surface of the sliding bore (10a) such that the communication groove (28) is capable of communicating with a space between said lifter (26) and said piston (16) at a position on that side of the seal member (14) which is close to the lifter (26). A valve operating system of an internal combustion engine according to claim 1, wherein a relief valve (30) is provided so as to be opened at a valve opening pressure corresponding to a maximum pressure in said air pressure chamber (13) which is achieved when a predetermined amount of lubricant oil has gathered in said air pressure chamber (13), said relief valve (30) being connected to the air pressure chamber (13) through a relief passage (29) which is provided in said sleeve (10) and is placed in communication with an interior of the air pressure chamber (13) at a position lower than a level of said predetermined amount of lubricant oil gathered within the air pressure chamber (13) and above said guide hole (10b). A valve operating system of an internal combustion engine according to claim 1 or 2, wherein said piston (16) is provided at a central position thereof with a tapered through hole (20) which is formed at one of opposite ends thereof to be larger in diameter than the other end to receive by press-fitting a cotter (19) for fixing said piston (16) to the valve shaft portion (5a), and a valve shaft seal member (22) made of elastic material and comprising a cylindrical portion of a substantially cylindrical shape for resilient fitting to the other end of said through hole (20) and a flange portion on the cylindrical portion for contact with the central portion of said piston (16) and provided on the cylindrical portion, said seal member (22) being disposed between an inner surface of the through hole (20) and an outer surface of the valve shaft portion (5a). A valve operating system of an internal combustion engine according to any of claims 1, 2 or 3, wherein seal member (14) is fitted around an outer surface of said piston (16) and comprises an annular seal member which is of a substantial U-shape in cross section and is opened toward said air pressure chamber (13) and which has a lip portion (14b) for slide contact at an outermost peripheral portion thereof with the inner surface of said sliding bore (10a). A valve operating system of an internal combustion engine according to any preceding claim, wherein said lifter (26) and said piston (16) are slidably fitted in the sliding bore (10a) at positions axially spaced from each other. A valve operating system of an internal combustion engine according to any preceding claim, wherein the outer diameter of the outer cylindrical portion (16a) of the piston (16) is such that between the outer cylindrical portion (16a) and the inner surface of the lifter (26) there is formed a minute annulus serving as said space.

Inventors: KOMATSU, TOSHIYASU, K.K. HONDA GIJUTSU KENKYUSHO, SHIBATA,MITSUHIRO, SHIBATA,MITSUHIRO, C/O K.K.HONDA GIJUTSU KENKYUSHO
Applicants: HONDA GIKEN KOGYO KABUSHIKI KAISHA
Application year: 1990
Main classification: F01L3
IPC codes: F01L1, F01M9, F01L3