JP6587156B2 - Rotor structure of vane type internal combustion engine - Google Patents

Description

  The present invention relates to a rotor structure of a vane type internal combustion engine that includes a vane and a rotor that can rotate within a housing, and has a structure that is inexpensive to manufacture.

  In general, a vane type internal combustion engine is formed between a housing, a rotor disposed rotatably in the housing, a groove formed in the rotor and rotated together with the rotor, and formed between the inner peripheral surface of the housing and the rotor. And a plurality of vanes for partitioning the hollow portion into a plurality of hollow chambers. In any one of the plurality of hollow chambers, high-temperature and high-pressure combustion gas is generated by the combustion stroke. The volume of each chamber is increased or decreased by the rotation of the rotor, and each chamber rotates its output shaft through its respective stroke.

  For example, in Patent Document 1, a rotor structure of a conventional vane type internal combustion engine is configured to sandwich a vane by combining a partition ring with a half moon seal. In Patent Document 2, there are 16 vane grooves formed in the rotor, and 16 vanes are slidably inserted into the vane grooves to divide the hollow chamber of the housing into 16 chambers.

JP 2001-115849 A JP-A-10-68301

  For example, in the vane pressing structure of Patent Document 1, a partition ring is attached between the housing and the center shaft, and the partition plate is moved toward the housing at the center ring so that the partition plate can slide around the center shaft. It is attached in a radial pattern. Each partition plate incorporates a seal at the tip, and the seal is biased toward the inner peripheral surface of the housing by a coil spring.

  In the vane pressing structure of Patent Document 2, a plurality of vanes are provided in a housing, and a roller-shaped guide is attached to each vane. The guide body is guided by the circular guide and rotates in the housing together with the vane. Thus, the vane is configured so as to be slidable on the inner peripheral surface of the housing at all times. Further, the vane is provided with a tip vane protruding from the vane body, and the tip vane is pressed against the inner peripheral surface of the housing by a spring disposed at the bottom of the tip vane so as to absorb the fluctuation of the gap.

  In either case, in order to maintain airtightness, it is required to increase the surface roughness and dimensional accuracy of each sliding component, which increases the cost. In particular, in Patent Document 2, there are as many as 16 vanes and vane grooves formed in the rotor, and the thickness of the vanes is thin and long. Therefore, since the vane groove is also narrow and deep, in the processing of the vane groove of the rotor, a large cost is required to secure the surface roughness and reduce the wear. Further, as the speed increases, the degree of wear of each component also increases, so that sufficient lubrication is required. If sufficient lubrication is to be configured, a complicated lubrication circuit may be formed, which also increases the cost, so there is not much possibility that it can actually be put into practical use.

  In view of the above, the present invention provides a rotor structure for a vane-type internal combustion engine that can be used practically and does not require high cost with an easy configuration.

The rotor structure of the vane type internal combustion engine according to the present invention is configured as follows. That is,
The invention according to claim 1 is formed in a housing, a main shaft disposed at a position eccentric with respect to an axis of the housing, a rotor supported by the main shaft and rotating together with the main shaft, and the rotor. A plurality of vanes slidably disposed in the plurality of vane grooves, wherein one end of the vane is configured to be slidable on the inner peripheral surface of the housing, and the other end of the vane is built in the rotor A rotor structure of a vane type internal combustion engine that presses an outer peripheral surface of a formed elastic ring, wherein the rotor is disposed on both sides of the center rotor and the center rotor, and is integrally assembled with the center rotor by rotor set pins It is characterized by being divided into a pair of side rotors to be found.

  According to this, the rotor is divided into a center rotor and a pair of side rotors. An elastic ring that slides the vane on the inner peripheral surface of the housing so as to be slidable is incorporated in one of the divided rotors. Since the vane groove is formed on one side of one of the divided rotors, the elastic ring storage position can be set flexibly. Moreover, since the center rotor and the pair of side rotors are assembled by driving the rotor set pins, the insertion positions of the plurality of rotor set pins with the respective rotor set pin holes formed in the rotor By clarifying the relationship with, for example, alignment marks, disassembly and reassembly performed after temporary assembly can be easily performed without causing a positional shift with respect to the original position at the time of temporary assembly. .

  The invention according to claim 2 relates to the invention according to claim 1, wherein the elastic ring is built in the pair of side rotors.

  According to this, since the rotor is divided into the center rotor and the side rotor, the elastic ring can press the vane in the vicinity of both ends in the longitudinal direction of the vane by incorporating the elastic ring into the side rotor. Therefore, the inclination of the vane due to the pressure on the vane in the explosion process can be prevented, and the airtightness of each chamber partitioned by the vane can be improved.

  The invention described in claim 3 relates to the invention of claim 1 or 2, characterized in that an insert formed in a thin plate shape into which the vane is inserted is disposed in the vane groove. Yes.

  According to this, when the insert is fitted into the vane groove, the surface roughness due to the finishing of the side wall of the vane groove can be reduced. Therefore, the manufacturing cost can be reduced and practical use can be achieved. Even if there is a sign that the wear of the rotor or vane will increase due to long-term use, it is possible to protect the rotor and vane by simply replacing the insert, so maintenance can be achieved at low cost and practical use Can be made possible.

  The invention according to claim 4 relates to the invention according to claim 3, wherein a recess is formed on a side surface of the vane groove, and a protrusion that is fitted into the recess is formed on the insert. It is characterized by.

  According to this, the insert can be fixed in the vane groove by inserting the protruding portion of the insert into the recess of the vane groove, thereby preventing the insert from moving with the vane or falling off the vane groove.

FIG. 1 is a side sectional view showing the internal structure of the engine. FIG. 2 is a perspective view showing the entire state where the rotor in FIG. 1 is assembled. 3A is a cross-sectional view showing the insert, FIG. 3B is a side view, and FIG. 3C is a view showing a state where the insert is assembled to the vane groove. FIG. 4 is a perspective view showing the divided rotor. FIG. 5 is a front sectional view showing the assembled state of the divided rotors. FIG. 6 is a front sectional view through the central shaft portion of the assembled engine.

  Embodiments of the vane type internal combustion engine of the present invention will be described below with reference to the drawings.

  FIG. 1 is a side cross-sectional view showing the inside of a vane type internal combustion engine (hereinafter referred to as an engine), and FIG. 2 is a perspective view showing the entire assembled state of the rotor.

  As shown in FIG. 1, the engine 1 includes a hollow housing 2 that is disposed between both sides of an outermost outer case 9. As shown in FIG. 6, the housing 2 is divided into a center housing 2A and side housings 2B and 2C arranged on both sides of the center housing 2A. The side housings 2B and 2C are screwed at the side surface of the center housing 2A. Has been.

  As shown in FIGS. 1 and 6, the center housing 2A is formed in a hollow cylindrical shape, and an inner peripheral surface 3 that is slidably contacted with a tip of a vane 20 to be described later is a true center about the center axis C1 of the center housing 2A. It is formed in a circular shape. In the center housing 2A, main shafts 4 and 4 having a center axis C2 are disposed at positions eccentric to the center axis C1 of the center housing 2A. The main shafts 4 and 4 are respectively divided into a pair from the outer sides of the side housings 2B and 2C toward the center housing 2A. Each of the main shafts 4 and 4 includes large diameter portions 4a and 4a, flange portions 4b and 4b, and rotor shaft portions 4c and 4c.

  On the other hand, a rotor 10 that rotates together with the main shaft 4 is disposed so as to face the inner peripheral surface 3 of the center housing 2A. As shown in FIGS. 2 and 4, the rotor structure K showing the characteristic configuration of the present invention is integrally formed by driving the divided rotor 10 with a plurality of rotor set pins 17 described later.

  As shown in FIG. 6, the rotor 10 is formed by dividing it into a center rotor 10 </ b> A and side rotors 10 </ b> B and 10 </ b> C disposed on both sides of the center rotor 10 </ b> A. FIG. 1 shows a view from the inner side surface of the side rotor 10C.

  Each of the side rotors 10B and 10C is screwed and fixed to the flange portions 4b and 4b of the main shafts 4 and 4, respectively. The center rotor 10A and each of the side rotors 10B and 10C are integrally formed by five rotor set pins 17. It is assembled to.

  The center rotor 10A is formed in a cylindrical shape, and a shaft hole 11A into which the rotor shaft portions 4c and 4c of the main shaft 4 are inserted from both sides is formed in the center portion of the center rotor 10A. In the center rotor 10A, a plurality of (in the embodiment, five) vane grooves 12A are formed at equal intervals in the radial direction from the outer peripheral surface to the inner side, and on the outer peripheral surface, in the vicinity of each vane groove 12A, A curved portion 13A for rotating in one direction with gas pressure is formed in a concave shape on the outer peripheral surface. Further, between the vane groove 12A and the curved portion 13A, rotor set pin holes 14A into which the five rotor set pins 17 are inserted are formed at five locations.

  The side rotors 10B and 10C are formed in a cylindrical shape like the center rotor 10A, and shaft holes 11B and 11C into which the rotor shaft portion 4c of the main shaft 4 is fitted are formed in the center portion. In the side rotors 10B and 10C, a plurality of (in the embodiment, five) vane grooves 12B and 12C are formed at equal intervals in the radial direction from the outer peripheral surface inward. On the outer peripheral surface, curved portions 13B and 13C for rotating in one direction by gas pressure are formed in the vicinity of the vane grooves 12B and 12C in a concave shape on the outer peripheral surface.

  Furthermore, between the vane grooves 12B and 12C and the curved portions 13B and 13C, rotor set pin holes 14B and 14C into which five rotor set pins 17 are respectively inserted are formed at five locations. In addition, on the inner end surfaces in the width direction of the side rotors 10B and 10C, elastic ring storage holes 15B and 15C into which the elastic rings 30 described later are inserted concentrically with the shaft holes 11B and 11C are respectively provided at predetermined depths from the inner end surfaces. Is formed.

  As shown in FIGS. 1-3, after vane groove | channel 12A, 12B, 12C has assembled | attached center rotor 10A and side rotor 10B, 10C, one vane 20 is inserted. As shown in FIG. 4, the vane 20 includes a vane main body portion 21 formed in a rectangular parallelepiped shape, a bottom portion 22 having one end formed in a round shape, and a seal groove portion formed in a tip portion 23 opposite to the bottom portion 22. 23a. As shown in FIG. 4, vanes 20 are slidably disposed in the vane grooves 12A, 12B, and 12C in the vane grooves 12A, 12B, and 12C of the center rotor 10A and the side rotors 10B and 10C. As shown in FIG. 3, the vane 20 is fitted into the vane grooves 12 </ b> A, 12 </ b> B, and 12 </ b> C via an insert 24 that slides on the side surface of the vane 20.

  The insert 24 is formed by mirror-finishing the sliding inner surface of the vane 20 and is formed in a thin-walled hollow shape so that the vane 20 can be inserted. The insert 24 has notches 24a at two positions on the left and right in the longitudinal direction. Curved protrusions 24b and 24b are provided on both upper sides in the height direction. The notch 24a is formed at a position where the vane 20 is pressed against an outer peripheral surface of an external elastic ring 32 described later when the insert 24 is inserted into the vane grooves 12A, 12B, 12C. Further, the protrusion 24b is fitted into the recesses 12a and 12a formed on the side wall portions of the vane grooves 12A, 12B, and 12C in order to prevent the protrusions 24b from falling off the vane grooves 12A, 12B, and 12C. By inserting the insert 24 into the vane grooves 12A, 12B, and 12C, surface roughness caused by finishing the side walls of the vane grooves 12A, 12B, and 12C of the rotors 10A, 10B, and 10C can be reduced.

  In a state where the center rotor 10A and the side rotors 10B and 10C are integrally assembled, the vane 20 is inserted after the insert 24 is fitted into the vane grooves 12A, 12B, and 12C. As shown in FIG. 6, the length in the width direction (longitudinal direction) inserted into the vane groove 12 of the vane 20 is substantially equal to the combined length of the center rotor 10A and the side rotors 10B and 10C.

  As shown in FIG. 4, a vane tip seal 25 is fitted into the seal groove 23a. The vane tip seal 25 may be always urged toward the inner peripheral surface 3 side of the housing 2 by elastic means such as a leaf spring (not shown) between the vane 20 and the seal groove 23a.

  The tip portion 23 of the vane 20 is formed in a flat shape, and the corner portion thereof is in sliding contact with the inner peripheral surface 3 of the housing 2, and the tip portion 25a of the vane tip seal 25 is formed in an arc shape on the inner peripheral surface 3 of the housing. In order to be slidably contacted, for example, it may be formed in a prismatic shape in which carbon is impregnated with metal.

  As shown in FIG. 1, the configuration for pressing the vane 20 against the inner peripheral surface of the housing 2 includes the housing 2, the rotor 10, and the elastic ring 30 supported by the vane 20 and the main shaft 4. ing. The vane 20 is disposed by an elastic ring 30 so that the inner peripheral surface 3 of the housing 2 can be pressed.

  More specifically, the bottom 22 of the vane 20 is in contact with the outer end surface of the elastic ring 30 supported by the rotor shaft 4c of the main shaft 4. Therefore, the vane 20 presses the inner peripheral surface 3 of the housing 2 with the tip portion 23 or the tip portion 25 a of the vane tip seal 25.

  The elastic ring 30 is inserted into the elastic ring receiving holes 15B and 15C of the pair of side rotors 10B and 10C, and comes into contact with portions projecting from the center rotor 10A of the vane 20 on both sides. Will be pressed to the inner peripheral surface 3 side.

  In the embodiment, the elastic ring 30 has an outer elastic ring 32 concentric with the rolling bearing 31 pressed into the outer ring side of the rolling bearing 31 and an inner elastic ring 33 pressed into the inner ring side of the rolling bearing 31. The inner elastic ring 33 is mounted on the rotor shaft portion 4c of the main shaft 4 so as to be idled at a position eccentric from the central axis C1 of the rolling bearing 31. The outer elastic ring 32 is tightly fitted to the outer ring of the rolling bearing 31 in order to rotate with the rotor 10, and rotates with respect to the inner elastic ring 33.

  Further, the bottom 22 of the vane 20 can bite into the outer peripheral surface of the external elastic ring 32, and further presses the vane 20 against the inner peripheral surface 3 of the housing 2 by its elasticity. Therefore, it is desirable that the outer elastic ring 32 be formed of a material having appropriate flexibility, for example, a urethane rubber material. Further, the inner elastic ring 33 is not particularly limited to an elastic body, but if it is the same material as the outer elastic ring, the inner peripheral surface 3 of the housing 2 and the vane 20 tip 23 or the vane tip seal 25 This is desirable because it can absorb more gaps with the tip 25a.

  In addition, the rolling bearing 31 becomes maintenance-free because no oil is used by using a grease-filled type.

  Next, a procedure for assembling the engine 1 configured as described above will be described.

  First, the rotor set pins 17 are driven and integrated in a state where the side rotors 10B and 10C in which the vane grooves 12A, 12B and 12C are in the rough processed state are overlapped with the center rotor 10A in which the vane grooves 12A are in the rough processed state. The rotor 10 made is assembled. The center rotor 10A, the side rotors 10B and 10C, and each rotor set pin 17 are marked so as to coincide with each position of the rotor set pin hole 14B (or 14C) formed in the side rotor 10B (or 10C). . Finishing of the side wall of the vane groove 12 assembled in this state is performed. After finishing, the rotor 10 is temporarily disassembled into a center rotor 10A and a pair of side rotors 10B and 10C by removing all the rotor set pins 17.

  Next, as shown in FIGS. 4 to 5, the elastic ring 30 is stored in the elastic ring storage holes 15B and 15C of the divided side rotors 10B and 10C, and the main shafts 4 and 4 are connected to the side rotors 10B and 10C. The shaft holes 11B and 11C and the shaft hole 33a of the elastic ring 30 (inner elastic ring 33) are inserted. Accordingly, the flange portions 4b and 4b and the side rotors 10B and 10C are screw-fastened in a state where the elastic ring 30 is built in the side rotors 10B and 10C. Then, the rotor shaft portions 4c and 4c of the side rotors 10B and 10C incorporating the main shafts 4 and 4 and the elastic ring 30 are inserted into the shaft hole 11A of the center rotor 10A and assembled as the rotor 10. Thereafter, the rotor set pin 17 is inserted into the marked rotor set pin hole 14 so as to be in the same position as before disassembly, and the rotor 10 is integrated. In this state, five inserts 24 (see FIG. 3) are inserted into the vane groove 12 from the outer peripheral side of the side rotor 10B (or 10C). Then, the vane 20 in which the vane tip seal 25 is inserted into the seal groove 23 a is inserted into the insert 24. The vane tip seal 25 may be inserted into the seal groove 23 a of the vane 20 after the vane 20 is fitted into the insert 24. The bottom portion 22 of the vane 20 is attached so as to contact the outer peripheral surface of the outer elastic ring 32 at the position of the notch portion 24 a of the insert 24. At this time, the outer diameter of the circle connecting the tip portions 23 of the vanes 20 is larger than the inner diameter of the inner peripheral surface 3 of the center housing 2A. The tip portions 25a of the five vane tip seals 25 are inserted into the inner peripheral surface 3 of the center housing 2A while being simultaneously pushed.

  Therefore, the elastic ring 30 is in a state where the inner elastic ring 33 is press-fitted into the inner ring of the rolling bearing 31 and the outer elastic ring 32 is pressed into the outer ring. Since the shaft hole 33a of the inner elastic ring 33 and the rotor shaft portions 4c and 4c of the main shaft 4 are fitted so as to be idle, the rotation of the main shaft 4 rotates the outer elastic ring 32 together with the outer ring of the rolling bearing 31.

  Thereafter, the center housing 2A and the side housings 2B and 2C are attached around the integrated rotor 10, and the engine 1 having the rotor 10 built in the integrated housing 2 is constructed as shown in FIG. To do.

  The rotor set pin 17 may be formed in a round bar shape, but if it is a spring pin partially having an opening along the axial direction, the inner peripheral surface of the rotor set pin holes 14A, 14B, 14C It is also possible to process with high accuracy. Hereinafter, the assembled center rotor 10A and side rotors 10B and 10C are also simply referred to as the rotor 10. The rotor 10 rotates in one direction by the rotation of the main shaft 4.

  Since the housing 2 is integrated with the center housing 2A and the side housings 2B and 2C, in the description of the integrated housing, hereinafter, the housing 2 will be simply referred to as the housing 2, and the sliding contact surface with the vane 20 will be referred to below. The inner peripheral surface 3 is assumed. Similarly, in the case of the rotor 10, when the rotor 10 is collectively shown, there may be cases where A, B, and C of 10A, 10B, and 10C are omitted.

  In the hollow portion 6 of the housing 2, a plurality of vanes 20 (five in the embodiment) are arranged. In the vane 20, since the elastic ring 30 presses the inner peripheral surface 3 of the housing 2 by the elasticity of the external elastic ring 32, the hollow portion 6 between the housing 2 and the rotor 10 is partitioned by the vane 20. A plurality of (in the embodiment, five chambers) hollow chambers (6A, 6B, 6C, 6D, 6E) for conveying the high-pressure gas are formed.

  Further, the inner elastic ring 33 is disposed on the main shaft 4 in an idle state, and the outer elastic ring 32 rotates around the central axis C1 of the housing 2 at a position eccentric from the main shaft 4. The deviation between the center axis C2 of the main shaft 4 and the rotational center position of the outer elastic ring 32 is absorbed by the vane 20 sliding in the vane groove 12 of the rotor 10. Therefore, at any position where the rotor 10 rotates, the vane 20 slides in the vane groove 12 by the eccentric amount, and one end of the vane 20 slides from the inner peripheral surface 3 of the housing 2. A substantially constant position is maintained at a position where the bottom 22 presses the outer peripheral surface of the external elastic ring 32. Accordingly, the inner elastic ring 33 is always maintained at a fixed position with respect to the housing 2.

  On the other hand, as shown in FIG. 1, the center housing 2A is provided with a fuel supply nozzle 7 for supplying fuel from the outer peripheral surface toward one of the hollow portions 6, and can be ignited toward another pressure chamber. A spark plug 8 is provided.

  In the engine configured as described above, in each of the hollow chambers 6A, 6B, 6C, 6D, and 6E, an explosion occurs once in two rotations of the rotor 10 due to the rotation of the rotor 10, during which expansion, exhaust, air intake The process of air compression, supercharging, scavenging, compressed air intake, and mixed gas compression is performed. In the case of the embodiment formed in five chambers, five explosions occur in two rotations of the rotor 10.

  In addition, since the above-mentioned process is the same as that of Japanese Patent No. 4827658 which is the previous application of the present applicant, the description thereof is omitted in the present invention.

  In any case, since the rotor 10 is divided into the center rotor 10A and the pair of side rotors 10B and 10C, it is difficult to process the vane groove 12 in the rotor 10 and set the elastic ring storage position while repeating assembly and disassembly. Can be easily performed. Further, the surface roughness of the vane groove 12 can be reduced by fitting the insert 24 into the vane groove 12. Therefore, a rotor structure that can be manufactured at low cost can be provided.

  Further, since the vane 20 is slidably in contact with the inside of the housing 2 while being constantly pressed by the elastic ring 30 against the inner peripheral surface of the housing 2, the airtightness of each hollow chamber is maintained. Moreover, since the elastic ring 30 is constituted by the outer elastic ring 32 on the outer ring side of the rolling bearing 31 and the inner elastic ring 33 on the inner ring side of the rolling bearing 31, the elastic ring 30 presses the vane that keeps airtightness in each hollow chamber. It can be configured simply and at a low cost, and if the rolling bearing is made of a grease-enclosed type, a less expensive airtight structure can be provided without providing a new lubrication structure. Can be provided.

  Since the present invention is configured so that the rotor can be divided and assembled so that machining accuracy and difficult machining inside the rotor can be easily manufactured at low cost, the vane shown in the embodiment is used. The pressing structure, the internal structure of the rotor, and the material and shape of the vanes are not limited.

DESCRIPTION OF SYMBOLS 1, Engine 2, Housing 2A, Center housing 3, Inner peripheral surface 4, Main shaft 4c, Rotor shaft part 10, Rotor 10A, Center rotor 10B, Side rotor 10C, Side rotor 11A, 11B, 11C, Shaft hole 12A, 12B, 12C, vane groove 14A, 14B, 14C, rotor set pin hole 15B, 15C, elastic ring storage hole 17, rotor set pin 20, vane 30, elastic ring C1, (housing) central axis C2, (main shaft) central axis K, rotor structure

Claims (4)

A housing, a main shaft disposed at an eccentric position with respect to the axis of the housing, a rotor supported by the main shaft and rotating together with the main shaft, and a plurality of vane grooves formed in the rotor. A plurality of vanes disposed on the housing, wherein one end of the vane is configured to be slidably contacted with an inner circumferential surface of the housing, and the other end of the vane is disposed on an outer circumferential surface of an elastic ring built in the rotor. The rotor structure of the vane type internal combustion engine to be pressed,
The rotor is divided into a center rotor and a pair of side rotors that are disposed on both sides of the center rotor and are integrally assembled to the center rotor by a rotor set pin. Type internal combustion engine rotor structure.   The rotor structure of a vane type internal combustion engine according to claim 1, wherein the elastic ring is built in the pair of side rotors.   The rotor structure of a vane type internal combustion engine according to claim 1 or 2, wherein an insert formed in a thin plate shape into which the vane is inserted is disposed in the vane groove.   4. A rotor structure for a vane type internal combustion engine according to claim 3, wherein a recess is formed on a side wall surface of the vane groove, and a protrusion is formed on the insert so as to be fitted into the recess.

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