ROTARY ENGINE

Abstract: A rotary engine is disclosed which comprises a rotor housing, a rotor fitted in the rotor housing so as to define a plurality of operating chambers in cooperation with the inner wall surface of the rotor housing and produce a planetary rotation of itself inside the rotor housing, apex seal members severally accommodated inside seal grooves formed at the apexes of the rotor along the axis of rotation of said rotor, and pressure means disposed between the respective apex seal members and the rotor so as to press the apex seal members against the inner wall surface of the rotor housing by virtue of the pressure of a gas emanating from the operating chambers.

Description: This invention relates to a rotary engine having improvements embodied in the apex seal parts which are attached to the apexes of the rotor thereof. Generally, a rotary engine has the rotor thereof disposed inside a rotor housing having a trochoidal inner wall surface formed with a major diameter part and a minor diameter part and has operating chambers partitioned and mutually sealed off by the apex seal members embedded one each in the grooves formed at the apexes of the rotor along the axis of rotation of the rotor. The rotary engine, for the purpose of keeping the adjacent operating chambers in a mutually sealed or airtight condition while the rotor is performing a planetary rotation inside the rotor housing, is required to be provided with such apex seal members as are capable of moving sensitively and infallibly relative to the radial direction of the rotor. Particularly, of the two apex seal members which happen to seal an operating chamber held in a state involving the stroke of compression to the stroke of explosive combustion, the apex seal member existing on the front side in the direction of advance relative to the rotation of the rotor is liable to suffer leakage of the compressed gas or the combustion gas from the operating chamber under discussion. The apex seal member on the front side, therefore, must therefore seal even more reliably. A rotary engine in accordance with the prior art portion of claim 1 is disclosed in Patent Abstracts of Japan, Vol 11, No 339 (M-639) [2786], 6 November 1987. The present invention, as defined in claim 1, provides a recess extending along the top portion of the apex seal which has the effect of reducing the force tending to depress the apex seal member. This improves the efficiency, as will later be described in greater detail, of the manner in which the apex seal members, during the planetary rotation of the rotor thereof, are able to move sensitively and infallibly relative to the radial direction of the rotor and maintain the necessary contact with the sliding surface of the rotor housing and keep the adjacent operating chambers in a gas tight state. The invention will be further described by way of non-limitative example with reference to the accompanying drawings, in which: Fig. 1 is a front cross-sectional view of a rotary engine. Fig. 2, Fig. 3, Fig. 4, and Fig. 5 are explanatory diagrams illustrating the manner of exertion of force upon an apex seal member. Fig. 6 is a partially sectioned view illustrating as magnified the portion A indicated in Fig. 1 of the rotary engine of this invention fitted with an apex seal member. Fig. 7 is a side elevational view for the cross section taken along line VII-VII in Fig. 6. Fig. 8 is a perspective view of corner seals of the rotary engine according with this invention. Fig. 9 is a partially sectioned view illustrating as magnified the portion A indicated in Fig. 1 of the rotary engine of the present invention fitted with other roller members for an apex seal member. Fig. 10 is a side elevational view for the cross section taken along line X-X in Fig. 9. Fig. 11 is a perspective view of roller members. Fig. 12 is a perspective view of an apex seal member. Fig. 13 is an explanatory diagram illustrating the manner of exertion of gas pressure upon an apex seal member in the rotary engine. Fig. 14 is a partially sectioned view illustrating as magnified the portion A indicated in Fig. 1 of another typical rotary engine as the second embodiment of this invention. Fig. 15 is a side elevational view for the cross section taken along line XV-XV in Fig. 14. Fig. 16 is a partially sectioned view illustrating as magnified the portion A indicated in Fig. 1 of yet another typical rotary engine as the third embodiment of this invention. Fig. 17 is a side elevational view for the cross section taken along line XVII-XVII in Fig. 16. Fig. 1 is a diagram illustrating in cross section a rotary engine. First, the various forces generally exerted on individual apex seal members while a rotor 11 is kept in planetary rotation will be described with reference to Fig. 1, Fig. 2, Fig. 3, Fig. 4, and Fig. 5. As shown in Fig. 2 which illustrates as magnified the portion A indicated in Fig. 1, an apex seal member 3 is fitted in a seal groove 4 which is formed at an apex 2 of the rotor 11. In the apex seal member 3 set in place as described above, a flow of gas indicated by an arrow 45 (Fig. 2), at pressure P1, and emanating from an operating chamber V1 held in a state of high pressure exerts a pressing force on one of the lateral sides 10 of the apex seal member 3 facing to the operating chamber V1 and causes the other lateral side 12 facing to an adjacent operating chamber V2 to be strongly pressed against one of the wall surfaces 6b of the seal groove 4 falling on the operating chamber V2 side, with the result that the movement of the apex seal member 3 relative to the radial direction indicated by an arrow 14 is inhibited to a great extent. Further, while the apex seal member 3 is positioned on the front side in the direction of advance relative to the rotation of the rotor 11 indicated by an arrow 13 in Fig. 2, since a top surface 28 of the apex seal member 3 is depressed toward a bottom surface 15 of the seal groove 4 and, at the same time, the other lateral side 12 facing the operating chamber V2 is strongly pressed against wall surface 6b of the seal groove 4 on the side of the operating chamber V2 by the pressing force exerted inwardly in the radial direction indicated by the arrow 14 by the gas flow indicated by an arrow 60, at pressure P1, and emanating from the operating chamber V1 held in a state of high pressure, the apex seal member 3 assumes a state locked by the frictional resistance generated between the lateral side 12 and the wall surface 6b. Thus, insufficient contact is established between the top surface 28 and the sliding surface 1 of the rotor housing 20, and a gap can occur between the top surface 28 and the sliding surface 1, thus allowing gas to pass from the operating chamber V1 the operating chamber V2. The apex seal member 3 of the foregoing description has the top surface 28 thereof shaped in an arched surface which, as illustrated in Fig. 3, has as the radius of curvature thereof the amount "a" of amplitude of the reciprocating motion produced by the top surface 28 relative to the direction indicated by the arrow 14 when the top surface 28 is moved as reciprocated parallelly to the sliding surface 1 (trochoidal inner wall surface) of the rotor housing 20. Since the apex seal member 3 is constructed as described above, a part 62 of the top surface 28 which contacts the sliding surface 1 is continuously moved over the entire arcuate surface of the top surface 28 in consequence of the rotation of the rotor 11 inducing uniform abrasion of the top surface 28. This enhances the wear resistance of the apex seal member 3. A spring 27 interposed between a bottom part 5 of the apex seal member 3 and the bottom surface 15 of the seal groove 4 exerts on the apex seal member 3 a pressing force produced outwardly in the radial direction indicated by the arrow 14. As illustrated in Fig. 4, while the rotor 11 is rotated inside the rotor housing 20 in the direction of the arrow 13, the inertial force originating in the centrifugal force generated outwardly in the radial direction indicated by the arrow 14 from the center P (Fig. 1) of rotation of the rotor 11 and accelerated in direct proportion to the rotational speed of the rotor 11 is exerted upon the apex seal member 3. Further, the gas pressure is retained in the state of P1 inside the operating chamber V1 and the gas pressure is retained in the state of P2 inside the operating chamber V2 (P1 > P2). On the apex seal member 3 are further exerted the combustion gas pressure indicated by an arrow 61 and transmitted from the operating chamber V1 through a passage 16 formed between the lateral side 10 of the apex seal member 3 and a wall surface 6a of the seal groove 4 and then through a chamber 19 and the compressed gas pressure, namely the pressing force produced by the pressure P1 of the gas inside the operating chamber V1 and exerted on the bottom part 5 of the apex seal member 3 outwardly in the radial direction indicated by the arrow 14 from the center P of rotation of the rotor 11 (Fig. 1). The pressing force by the pressure P1 of the gas described above is acting in a large proportion on the apex seal member 3. The force, F, which is acting on the entirety of the apex seal member 3 is expressed by the following formula: F = P1A3 - (P1A1 + P2A2) - µP1A4 wherein P1 stands for the inner pressure of the compression-combustion side operating chamber (high pressure side), P2 for the inner pressure of the exhaust side operating chamber (low pressure side), A1 for the pressure-receiving area of the top surface 28 of the apex seal member 3 on which the pressure P1 acts, A2 for the pressure-receiving area of the top surface 28 of the apex seal member 3 on which the pressure P2 acts, A3 for the pressure-receiving area of the bottom part 5 of the apex seal member 3 on which the pressure P1 acts, A4 for the pressure-receiving area of the lateral side 10 of the apex seal member 3 on which the pressure P1 acts, and µ for the friction coefficient between the lateral side 12 of the apex seal member 3 and the wall surface 6b of the seal groove 4. The term "P1A3" in the formula represents the force which, by virtue of the gas pressure P1 introduced via the passage 16 into the chamber 19 of the seal groove 4, pushes up the apex seal member 3 outwardly in the radial direction indicated by the arrow 14 and causes the top surface 28 of the apex seal member 3 to come into fast contact with the sliding surface 1 of the rotor housing 20. The term "P1A1 + P2A2" in the formula represents the force which acts on the top surface 28 of the apex seal member 3 to depress the apex seal member 3 inwardly in the radial direction indicated by the arrow 14 and tend to separate the top surface 28 from the sliding surface 1 of the rotor housing 20. The term "µP1A4" in the formula represents the sliding friction resistance which is generated between the lateral side 12 of the apex seal member 3 and the wall surface 6b of the lateral side while the apex seal member 3 is pressed against the wall surface 6b on one side of the seal groove 4 by the gas pressure P1. Despite the gas pressure introduced into the chamber 19 formed between the bottom part 5 of the apex seal member 3 and the bottom surface 15 of the seal groove 4, the flow resistance offered in the inlet passage 16, the change in volume of the inlet passage 16, the change in the gas pressure P1 itself, etc. cooperate to prevent the top surface 28 of the apex seal member 3 from being pressed with sufficient force against the sliding surface 1 of the rotor housing 20. Thus, there is the possibility that the important force P1A3 for raising the apex seal member 3 into good contact with the sliding surface 1 of the rotor housing 20 and keeping the adjacent operating chambers V1 and V2 mutually sealed in an airtight state will be insufficient relative to the force P1A1+P2A2 tending to separate the apex seal member 3 from the sliding surface 1 of the rotor housing 20 and the force µP1A4 of the frictional resistance concerning the motion of the apex seal member 3 in the radial direction indicated by the arrow 14. Particularly where the radius of curvature of the top surface 28 of the apex seal member 3 is large, namely the height "a" of the arch top surface 28 in the radial direction indicated by the arrow 14 is large, the combustion gas of high pressure P1 is suffered to act on the area A1, i.e. a relatively wide area on the top surface 28 of the apex seal member 3 on the front side in the direction of advance relative to the rotation of the rotor 11 indicated by the arrow 13 while the operating chamber V1 in the process of operation for compression and combustion. Thus, there is the possibility that the aforementioned force P1A3 be small as compared with the force, P1A1+P2A2, which is acting on the top surface 28 of the apex seal 3. This is because the part 62 of the arch top surface 28 of the apex seal member 3 which contacts the sliding surface 1 of the rotor housing 20 approaches an apex part 63 of the top surface 28 in consequence of the rotation of the rotor 11 and, as the result, the high pressure P1 of the combustion gas eventually acts on a wide region of the top surface 28. The apex seal member 3 tends to be raised by the aforementioned centrifugal force, the force P1A3 (lifting force), and the repulsive force generated outwardly in the radial direction indicated by the arrow 14 by the spring 27 serving to lift the apex seal member 3. The force, P1A1+P2A2 acting on the top surface 28 of the apex seal member 3 and the force of frictional resistance, µP1A4, prevent the apex seal member 3 from being sufficiently raised or force it to remain still, with the result that a gap can form between the top surface 28 of the apex seal member 3 and the sliding surface 1 of the rotor housing 20. The combustion gas of high pressure P1 and the unburnt compressed gas pressed by the combustion gas can then leak through gap into the neighbouring operating chamber V3 which is in the process of emitting exhaust gas. This leakage possibly lowers the engine output and degrades the efficiency of fuel consumption. Now, the abrasion of the top surface 28 of the apex seal member 3 will be described below with reference to Fig. 5. When the apex seal member 3 slides over the sliding surface 1, namely the trochoidal inner wall surface, of the rotor housing 20, abrasion tends to be concentrated at the apex part 63. As the result, the top surface 28 of the apex seal member 3 is abraded to a greater depth in the opposite parts 64, 65 outside the apex part 63 as indicated by a two-dot chain line 66 in Fig. 5 and, therefore, is gradually rounded and thinned. The length of the arch of the top surface 28 of the apex seal member 3 gradually increases and the area of the top surface 28 which receives the gas pressure acting on the top surface 28 gradually widens and the depth of the depression of the apex seal member 3 proportionately increases. The forces which act on the apex seal member and the motion imparted by the forces to the apex seal member have been described. In the rotary engine of this invention, the various forces acting on the apex seal members as described above can be varied to advantage as described below by the improvements contemplated by this invention and embodied in the apex seal members. With reference to Fig. 1, Fig. 6, and Fig. 7, 1 stands for a rotary a sliding surface of the rotor housing 20, 2 for an apex part of the rotor 11, 3 for an apex seal member, 4 for a seal groove, 5 for a bottom part of the apex seal member 3, 6a and 6b each for a wall surface of the seal groove 4, 8 for a roller, and 30 for a corner seal. As illustrated in Fig. 1, the rotor 11 revolves around the output shaft P of rotation and, at the same time, rotates on a rotor journal 67 deviating from the center of the output shaft P and the vicinity of the apex parts 2 of the rotor 11 slide over the sliding surface 1 of the rotor housing 20 in a state retaining contact with the sliding surface 1. Thus, the operating chambers V1, V2, and V3 for performing the steps of operation, i.e. suction, compression, combustion, expansion, and exhaust are formed between the sliding surface 1 of the rotor housing 20 and the periphery of the rotor 11. The states of airtightness of these operating chambers V1, V2, and V3, therefore, are maintained by eliminating gas leakage through the gap between the apex parts 2 of the rotor 11 and the sliding surface 1 of the rotor housing 20 and the gap between the lateral side 32 of the rotor 11 and a side housings 40 (Fig. 7). As illustrated in Fig. 6 and Fig. 7, therefore, the seal grooves 4 are formed one each at the apex parts 2 and the apex seal members 3 are disposed one each in the seal grooves 4 so as to preclude the otherwise possible occurrence of the gap between the apex parts 2 and the sliding surface 1. Side seals 68 are disposed on the opposite sides 32 of the rotor 11 and, at the same time, the corner seals 30 are interposed between the apex seal member 3 and the side seals 68 so as to preclude the otherwise possible occurrence of the gap between the lateral sides 32 and the side housings 40. Thus, the mutual airtightness of the operating chambers V1, V2, and V3 is maintained. In the chamber 19 formed between the bottom surface 15 of the seal groove 4 and the bottom part 5 of the apex seal member 3, the spring 27 is disposed so as to press the apex seal member 3 elastically against the sliding surface 1. Groove like depressions 7 are formed one each in the wall surfaces 6a, 6b of the seal groove 4 opposed respectively to the lateral sides 10, 12 of the apex seal member 3. A plurality of slender rollers 8 are rotatably accommodated in the depressions 7. These rollers 8 are so adapted that they are allowed to maintain rolling contact with the lateral sides 10 and 12 even when the apex seal member 3 is moved relative to the radial direction indicated by the arrow 14 and the lateral sides 10, 12 are exposed to the gas pressure emanating from the operating chamber. Various test results indicate that two rollers 8 are advantageously accommodated in each of the depressions 7. Desirably, the rollers 8 are made of a metallic material which is not easily softened or deteriorated by the gas of high pressure and high temperature and is not agglutinated or chemically degenerated by the product of combustion e.g. high-speed steel. The rollers 8 generally have a slender shape. Desirably they are formed in the shape of a cylindrical pin having a diameter approximately in the range of 1 to 0.5 mm. The rollers 8 are supported in place, as illustrated in Fig. 7, by having the opposite end parts 69 accommodated in the recesses 70 of a pair of corner seals 30 formed as illustrated in Fig. 8 and disposed one each at the opposite end parts of the rotor 11. The corner seals 30 are each provided with a groove 33 for accommodating the apex seal member 3 and are allowed to contact the side seals 68 on the outer wall surfaces 72 of the corner seals 30. The end faces 71 of the corner seals 30 are disposed as juxtaposed to the apex parts 2 at the opposite end parts of the rotor 11 so as to confront and slide over the inner surfaces 73 of the side housings 40. The rollers 8 are set inside the depressions 7 formed one each in the wall surfaces 6a, 6b of the seal groove 4 and adapted to support rotatably the apex seal member 3 and enable the apex seal member 3 to be smoothly moved in the radial direction indicated by the arrow 14 even when the apex seal member 3 is pressed against the wall surface 6b by the combustion gas pressure P1 of high magnitude. Optionally, the rollers 8 may be constructed as illustrated in Fig. 9, Fig. 10, and Fig. 11, so as to ensure introduction of the gas pressure P1 into the chamber 19 of the seal groove 4. Specifically, a pair of rollers formed by combining a roller 50 and a roller 51 as illustrated in Fig. 11 may be used in the place of the aforementioned plurality of rollers 8. The roller 50 on the upper side has the same shape as the roller 8. The roller 51 on the lower side is a grooved roller having a groove 52 formed on the outer periphery surface thereof. A plurality of grooves may be formed parallelly or one groove may be formed spirally. The roller 50 on the upper side is so adapted that when the apex seal member 3 is pressed by the gas pressure P2 against the wall surface 6a on one side of the seal groove 4, it will contact the wall surface 6a and the lateral side 10 of the apex seal member 3 and give rise to an airtight part and aid in the prevention of gas leakage. The roller 51 on the lower side is so adapted that when the apex seal member 3 is pressed against the wall surface 6b on one side of the seal groove 4 by the gas pressure P1, the groove 52 in the roller 51 forms a gas passage indicated by the arrow 45 and enables the gas pressure P1 to be introduced into the chamber 19 in the seal groove 4. If, in the present embodiment, the upper roller 50 and the lower roller 51 are both cylindrical rollers similarly to the rollers 8,while the upper roller 50 is enabled to move toward either of the opposite sides, namely the depression7 and the lateral side 10 of the apex seal member 3, and give rise to a gap capable of passing gas owing to the gap between the roller 50 itself and the depression 7 and the lateral side 10 of the apex seal member 3, the lower roller 51 can come into fast contact with the bottom part of the depression 7 and the lateral side 10 of the apex seal member 3 and fails to form a gas passage when the chamber 19 of the seal groove 4 is in the state of low pressure and is exposed to the action of the high-pressure gas entering the seal groove 4 through said gap of the upper roller 50. To avoid this possible misfortune, the lower roller 51 is so constructed as to form the groove 52 on the outer periphery surface thereof and ensure provision of a gas passage. Since the apex seal member 3 has the lateral sides 10, 12 thereof supported in place rotatably by the rollers 50, 51 as described above, it is enabled to move smoothly relative to the radial direction indicated by the arrow 14 even when the pressure of the gas emanating from the operating chamber strongly presses the lateral sides 10, 12 against the wall surfaces 6a, 6b of the seal groove 4. Moreover, since the gas from the operating chamber is infallibly introduced into the chamber 19 of the seal groove 4 through the groove 52 formed on the outer periphery surface of the roller 51, the apex seal member 3 is pushed up by the pressure of the incoming gas without fail outwardly relative to the radial direction indicated by the arrow 14. Further, in the arch apex part 63 on the top surface 28 of the apex seal member 3, a recess 9 is formed along the direction in which the axis of rotation of the rotor 11 is extended as illustrated in Fig. 12. Desirably, this recess 9 is constructed so that the width 24 thereof will fall in the range of 1/6 to 1/3 (0.5 to 1.0 mm) of the thickness 23 of the apex seal member 3 and the depth 25 thereof will fall in the range of 1.0 to 1.5 mm. The radius "a" of the arch part of the top surface 28 embracing the recess 9 (Fig. 3) is desired to be not less than 1.5 mm, a size larger than that of the apex seal member 3 of ordinary run. The top surface 28 of the apex seal member 3 in which the recess 9 is formed is divided into two rounded surfaces 10a, 10b formed on the opposite sides of the arch apex part 63 as opposed to each other across the recess 9. The apex seal member 3 is provided on the bottom part 5 thereof with protrusions 26 intended to facilitate the positioning of the apex seal member 3 relative to the direction of the aforementioned extension of the axis of rotation when the apex seal member 3 is fitted in the seal groove 4 formed in the rotor 11. While the rotor 11 is rotating inside the rotor housing 20, the angles of vibration of the apex seal members 3 relative to the sliding surface 1 of the rotor housing 20 vary and the parts 62 in which the two rounded surfaces 10a, 10b contact the sliding surface 1 of the rotor housing 20 vary. In other words, the two rounded surfaces 10a, 10b alternately come into contact with the sliding surface of the rotor housing 20. Particularly when the operating chamber V1 is in the initial process of combustion, the apex seal member 3 positioned on the front side of the operating chamber V1 relative to the direction of rotation of the rotor 11 has the rounded surface 10a held in sliding contact with the sliding surface 1 of the rotor housing 20 as illustrated in Fig. 6. As the rotation of the rotor 11 further proceeds from this state, the part 62 of contact gradually shifts to the rounded surface 10b (toward assuming the state of Fig. 13). Since the top surface 28 of the apex seal member 3 which is exposed to the action of the high-pressure gas of the operating chamber V1 in the process of combustion and expansion is provided with the recess 9, it has the rounded surface 10a first held in sliding contact with the sliding surface 1 of the rotor housing 20. While the top surface 28 is in this state, the part of a very narrow area faces the side of the operating chamber V1 now held in the state of high pressure (Fig. 6) and the recess 9 and the rounded surface 10b on the other side of the part of contact 62 face the operating chamber V2 now in the process of exhaustion. Thus, the gas of high pressure is acting on the part of narrow area and the gas of relatively low pressure on the part of relatively wide area embracing the recess 9 and the rounded surface 10b. When the rotor 11 is further rotated and part of contact 62 moves past the recess 9 of the top surface 28 and assumes a position on the rounded surface 10b as illustrated in Fig. 13, the pressure of the gas acting on the rounded surface 10a and the recess 9 is relatively low. As the result, the force tending to depress the apex seal member 3 toward the bottom surface 15 of the seal groove 4, namely inwardly in the radial direction indicated by the arrow 14 can be repressed to a small magnitude. The force which is generated by the pressure of the gas introduced via the passage 16 and is exerted upon the bottom part 5 of the apex seal member 3 in the direction of pushing up the apex seal member 3 outwardly in the radial direction indicated by the arrow 14, therefore, surpasses the pressing force tending to depress the apex seal member 3 as described above. As the result, the top surface 28 of the apex seal member 3 is pressed so fast against the sliding surface 1 of the rotor housing 20 that the airtight contact established therebetween can be safely retained. In the place of the construction which ensures safe introduction of the gas from the operating chamber into the chamber 19 of the seal groove 4 through the medium of the groove 52 formed on the outer periphery surface of the roller 51 as illustrated in Fig. 9 and Fig. 13, this invention further contemplates a construction which places in the depressions 7 formed in the seal groove 4 of each of the apex parts 2 of the rotor 11 such rollers 8 as formed in the shape of a cylindrical pin similarly to the rollers used in the embodiment of Fig. 6 and Fig. 7 and forms in the bottom parts 54 of the depressions 7 supporting the rollers 8 such recess 53 as adapted to communicate with the chamber 19 of the seal groove 4 as illustrated in Fig. 14 and Fig. 15 and warrants the safe introduction of the gas from the operating chamber into the chamber 19 of the seal groove 4 through the medium of the recess 53. In the place of the construction of the embodiment illustrated in Fig. 9 and Fig. 13, as shown in Fig. 16 and Fig. 17, the present invention further contemplates a construction in which the grooves 70 of the corner seals 30 illustrated in Fig. 8 disposed as opposed to the opposite, corresponding to the end parts 56 of a plurality of rollers 8 are adapted to support the rollers 8 and the depressions 7 are formed so that gaps 57 will occur between the rollers 8 and the bottom parts 54 of the depressions 7 while the rollers are held in the grooves 70 as described above. The gaps 57 are creatd throughout the entire areas of the depressions 7 relative to the longitudinal direction of the rotor 11 and allowed to communicate with the chamber 19 of the seal groove 4. The introduction of the gas indicated by the arrow 45 from the operating chamber to the chamber 19 of the seal groove 4 is ensured through the medium of the gaps 57.

Claims: A rotary engine having an apex seal member (3) the engine comprising: a rotor housing (20) having an inner wall surface (1); a rotor (11) disposed rotatably in said rotor housing so as to define a plurality of operating chambers (V₁,V₂) in cooperation with the inner wall surface (1) of said rotor housing, said rotor having apexes (2) and seal grooves (4) formed in said apexes respectively, parallel with the axis of rotation of said rotor; and an apex seal member (3) accommodated inside each one of said seal grooves (4), a chamber (19) being disposed between said apex seal member (3) and said rotor (11) so that said apex seal member (3) is pressed against said inner wall surface (1) of said rotor housing (20) by virtue of the of gas pressure emanating from an operating chamber, characterised in that each apex seal member has an open recess (9) extending along the top portion of said apex seal member so that the force tending to depress the apex seal member inwardly in the radial direction can be repressed to a small magnitude. A rotary engine according to claim 1, wherein said apex seal member (3) has a bottom part and pressing means (19) is provided with a gas passage means (16) disposed between said seal groove (4) and said apex seal member (3) communicates the gas pressure emanating from said operating chambers (V₁,V₂) to the chamber (19) to act on the bottom of said apex seal member. A rotary engine according to claim 2, wherein said seal groove (4) includes lateral wall surfaces (6a,6b) and a bottom wall surface (15), and said apex seal member has lateral sides (10,12), said gas passage means comprising gaps (16) formed between the lateral sides of said apex seal member and the lateral wall surfaces of said seal grooves. A rotary engine according to any preceding claim, wherein said seal grooves (4) have inner wall surfaces and said apex seal member (3) has lateral sides (10,12), said rotary engine further comprises means (8) for reducing frictional resistance interposed between the lateral sides (10,12) of said apex seal member (3) and inner wall surfaces (6a,6b) of said seal grooves (4) so as to decrease frictional resistance generated between said lateral sides and said inner wall surfaces. A rotary engine according to claim 4, wherein said inner wall surfaces of said seal groove (4) includes lateral wall surfaces (6a,6b) and said means for reducing frictional resistance comprises grooves (7) formed in the lateral wall surfaces of said seal groove and a plurality of roller members (8) accommodated in said grooves (7) and disposed with their axes along the direction of extent of said grooves. A rotary engine according to claim 5, when appendant to claim 2 or 3, wherein said gas passage means is further provided by the grooves (7) formed in the lateral walls surfaces (6a,6b) of said seal grooves (4) which are so formed so as to give rise to gaps between said grooves (7) and said roller members (8).

Inventors: BANDO, YOSHIHIRO
Applicants: BANDO KIKO CO., LTD
Application year: 1988
Main classification: F01C19
IPC codes: F01C19