JP6052748B2 - Drive device having XY separation crank mechanism - Google Patents

Description

  Embodiments of the present invention relate to a drive device including an XY separation crank mechanism that converts a reciprocating motion into a rotational motion and transmits the rotational motion, and converts a rotational motion into a reciprocating motion and transmits the same.

  A crank mechanism is known as a mechanism that converts a reciprocating motion into a rotational motion and transmits it. For example, an engine, a compressor, and the like include a piston that is reciprocally movable in a cylinder, a connecting rod that is rotatably connected to the piston, and a crankshaft that extends in a direction perpendicular to the reciprocating direction of the piston. ing. The other end of the connecting rod is rotatably connected to a crank pin provided eccentrically on the crankshaft. When the piston reciprocates in the cylinder, the reciprocating motion is converted into a rotational motion of the crankshaft by the swinging of the connecting rod and the eccentric rotation of the crankpin.

  In the crank mechanism having the above-described configuration, the connecting rod is normally rotatably connected to the piston via a piston pin, and moves in parallel while swinging around the piston pin during power transmission. Therefore, a rotational force is applied to the piston, and a wedge-effect friction loss is generated on the inner surface of the cylinder at two locations, the upper and outer peripheral portions of the piston. Usually, by reducing this friction loss with a lubricant, smooth reciprocation of the piston is possible. However, large pistons may run out of oil and appear as a seizure phenomenon.

  Conventionally, in order to reduce such seizure due to friction loss, a drive mechanism in which a cross head is provided between a piston and a connecting rod, or a small engine using a short piston has been proposed.

  However, although it is possible to increase the sealing degree of the piston by providing the cross head, the cross head also causes a friction loss that changes every 180 degrees due to the wedge effect at two locations. Therefore, although the reciprocating motion is performed as an operation, it becomes a vibration and causes a loss.

JP 2006-307961 A JP 2004-316576 A JP 2007-270653 A

  An object of an embodiment of the present invention is to provide a drive device that reduces friction loss and vibration and has high operation efficiency.

According to the embodiment, the drive device includes a first cylinder provided in a first installation plane located on one side of the center reference plane, and a reciprocating movement along the first direction in the first installation plane. A first piston provided in the first cylinder, a first crankshaft extending perpendicular to the first installation plane, and between the first piston and the first crankshaft in the first installation plane A first XY separation crank mechanism provided for reciprocally converting the reciprocating motion of the first piston and the rotational motion of the first crankshaft;
A second cylinder provided in a second installation plane located opposite to the center reference plane and symmetrically with respect to the first installation plane with respect to the center reference plane; and in the second installation plane, A second piston provided in the second cylinder so as to freely reciprocate along a second direction symmetrical to the first direction, a second crankshaft extending perpendicular to the second installation plane, and the second installation A second XY separation crank mechanism that is provided between the second piston and the second crankshaft in a plane and converts the reciprocating motion of the second piston and the rotational motion of the second crankshaft to each other;
A coupling synchronization mechanism that couples the first crankshaft and the second crankshaft, and rotates the first crankshaft and the second crankshaft in synchronization with each other.
The first XY separation crank mechanism is reciprocally movable along a first support member provided to be reciprocally movable in the first direction and a third direction orthogonal to the first direction in the first installation plane. A first crank connecting member, which is attached to the first support member and in which a crank of the first crankshaft is rotatably engaged, and the first piston and the first support member are connected to each other. The second XY separation crank mechanism in a fourth direction perpendicular to the second direction in the second installation plane, and a second support member provided to be reciprocally movable in the second direction. A second crank connecting member that is attached to the second support member so as to be reciprocally movable along the second crankshaft, and that a crank of the second crankshaft is rotatably engaged with, the second piston, and the second support member; Concatenate And it includes a second connecting member.

FIG. 1 is a perspective view showing a driving apparatus according to the first embodiment. FIG. 2 is an exploded perspective view showing the first drive unit of the drive device in an exploded manner. FIG. 3 is a side view schematically showing a state in which the first piston and the second piston of the driving apparatus have moved to top dead center. FIG. 4 is a side view schematically showing a state in which the first piston and the second piston of the drive device have moved in the direction of bottom dead center. FIG. 5 is a perspective view showing a driving apparatus according to the second embodiment. FIG. 6 is a perspective view showing a driving apparatus according to the third embodiment. FIG. 7 is a perspective view showing a driving apparatus according to the fourth embodiment. FIG. 8 is a side view showing a driving apparatus according to a fifth embodiment. FIG. 9 is a perspective view showing a driving apparatus according to the sixth embodiment. FIG. 10 is a perspective view showing a driving apparatus according to the seventh embodiment. FIG. 11 is a perspective view showing a driving apparatus according to the eighth embodiment. FIG. 12 is a perspective view showing a driving apparatus according to the ninth embodiment. FIG. 13 is a perspective view showing a driving apparatus according to the tenth embodiment. FIG. 14 is an exploded perspective view showing an XY separation crank mechanism of the driving apparatus according to the tenth embodiment. FIG. 15 is a diagram showing, in comparison with the crank connection member according to the tenth embodiment, and the crank connection member according to the comparative example, the deformation state of the crank connection member when stress is applied to the sliding surface. FIG. 16 is a perspective view showing the front side of the drive device according to the eleventh embodiment. FIG. 17 is a perspective view showing the back side of the drive device according to the eleventh embodiment. FIG. 18 is a partially cutaway front view of the drive device according to the eleventh embodiment. FIG. 19 is an exploded perspective view showing an XY separation crank mechanism of the drive device according to the eleventh embodiment. FIG. 20 is a perspective view showing the front side of the drive apparatus according to the twelfth embodiment. FIG. 21 is a perspective view showing the back side of the driving apparatus according to the twelfth embodiment. FIG. 22 is a partially cutaway front view of the drive device according to the twelfth embodiment. FIG. 23 is an exploded perspective view showing an XY separation crank mechanism of the drive device according to the twelfth embodiment. FIG. 24 is a diagram schematically illustrating an example of an intake / exhaust mechanism of a drive device according to a twelfth embodiment. FIG. 25 is a diagram schematically showing a modification of the intake / exhaust mechanism of the drive device according to the twelfth embodiment. FIG. 26 is a diagram showing a comparison between a displacement formula of a slider crank mechanism having a conventional connecting rod and a displacement formula of an XY separation crank mechanism according to the present embodiment. FIG. 27 is a diagram illustrating an equation for dynamic analysis of the XY separation crank mechanism according to the present embodiment. FIG. 28 is a diagram showing an equation for dynamic analysis of the slider crank mechanism. FIG. 29 is a diagram comparing vibration analysis results for a conventional slider crank mechanism and an XY separation crank mechanism according to the present embodiment.

  Hereinafter, various drive devices including the Z mechanism XY separation crank mechanism according to the embodiment will be described with reference to the drawings. In addition, the same code | symbol shall be attached | subjected to a common structure through embodiment, and the overlapping description is abbreviate | omitted. In addition, each drawing is a schematic diagram for promoting the embodiment and its understanding, and its shape, dimensions, ratio, etc. are different from the actual device, but these are considered in consideration of the following description and known techniques. The design can be changed as appropriate.

(First embodiment)
FIG. 1 is a perspective view of the drive device according to the first embodiment, and FIG. 2 is an exploded perspective view showing the first drive unit of the drive device in an exploded manner.
In the present embodiment, the drive device is configured as an engine or a compressor, for example. As shown in FIG. 1, the drive device 10 includes a first drive unit 20a having a first crankshaft 12a, a second drive unit 20b having a second crankshaft 12b, a first crankshaft 12a, and a second crankshaft. 12b, and a connection synchronization mechanism 50 that rotates the first crankshaft and the second crankshaft in synchronization with each other.

  The first drive unit 20a and the second drive unit 20b have the same configuration. The first drive unit 20a and the second drive unit 20b are respectively disposed on both sides of the center reference plane CRP, and further, the first drive unit 20a and the second drive unit 20b are left and right, front and rear with respect to the center reference plane CRP. They are arranged symmetrically (mirror arrangement) and configured.

  In the present embodiment, the first drive unit 20a is located on one side of the center reference plane CRP and is disposed in the first installation plane MP1 and the first cylinder 22a provided on the first installation plane MP1 orthogonal to the center reference plane CRP. A first piston 24a provided in the first cylinder 22a so as to be capable of reciprocating along the first direction, a first crankshaft 12a extending perpendicular to the first installation plane MP1, and a first piston in the first installation plane MP1. 1st XY separation crank mechanism 30a provided between 1 piston 24a and the 1st crankshaft 12a, and converting mutually the reciprocating motion of the 1st piston 24a, and the rotational motion of the 1st crankshaft 12a. . The first piston 24a is a piston having a circular cross section.

  In the present embodiment, the first direction, which is the reciprocating direction of the first piston 24a, is the first direction X1 orthogonal to the center reference plane CRP. The first crankshaft 12a is disposed substantially parallel to the center reference plane CRP.

  The second drive unit 20b is located on the opposite side of the center reference plane CRP and is disposed in the second direction within the second installation plane MP2 and the second cylinder 22b provided on the second installation plane MP2 orthogonal to the center reference plane CRP. A second piston 24b provided in the second cylinder 22b so as to be capable of reciprocating along, a second crankshaft 12b extending perpendicular to the second installation plane MP2, and a second piston 24b in the second installation plane MP2. A second XY separation crank mechanism 30b is provided between the second crankshaft 12b and converts the reciprocating motion of the second piston 24b and the rotational motion of the second crankshaft 12b to each other. The second piston 24b is a piston having a circular cross section.

  The second installation plane MP2 is located symmetrically with the first installation plane MP1 with respect to the center reference plane CRP. The second direction, which is the reciprocating direction of the second piston 24a, is a direction symmetric to the first direction X1 described above, and is a second direction X2 orthogonal to the center reference plane CRP. The first direction X1 and the second direction X2 form an angle of 180 degrees, that is, the same direction, and the first piston 24a and the second piston 24b are arranged coaxially with each other.

  As shown in FIGS. 1 and 2, the first crankshaft 12a of the first drive unit 20a is rotatably supported at both axial ends by bearings (not shown). A set of crank webs 14a is fixed in the middle of the first crankshaft 12a, and a crank pin 16a is fixed between the crank webs 14a. The center axis of the crank pin 16a is located parallel to the first crank shaft 12a and eccentric with respect to the center axis of the first crank shaft. The crankpin 16a rotates eccentrically around the first crankshaft 12a according to the rotation of the first crankshaft 12a.

  The first XY separation crank mechanism 30a is provided between the first piston 24a and the first crankshaft 12a, and performs reciprocating motion along the first direction X1 of the first piston 24a and rotational motion of the first crankshaft 12a. It is configured to convert and transmit to each other.

  The first XY separation crank mechanism 30a is a first support member (not shown) that is reciprocally movable along a first direction X1 on a first installation plane MP1 including a central axis (movement axis, X axis) of the first piston 24a. L-type combinator) 32a and a first crank connection attached to the first support member 32a so as to be reciprocally movable along a third direction Y1 (Y-axis direction) orthogonal to the first direction X1 in the first installation plane MP1. A member (crank connection plate) 34a and a connecting rod 36a as a connecting member for connecting the first piston 24a and the first support member 32a are provided. The movement center axis (first direction X1) of the first support member 32a, the movement center axis (third direction Y1) of the first crank connecting member 34a, and the center movement axis (first direction X1) of the first connecting rod 36a are as follows. , Located on the first installation plane MP1.

  The first support member 32a is formed, for example, in an L shape, and extends in the first direction X1, and extends in the third direction Y1 from one end (here, the left end) of the first support portion 33a. It has 2 support part 33b integrally. The first linear slider 40a is fixed to the first support portion 33a. A guide rail 44a is installed on the inner surface of the housing (not shown) and extends in the first direction X1 within the first installation plane MP1. The first linear slider 40a is supported and guided by the guide rail 44a so as to reciprocate. Thereby, only the 1st support part 33a among the 1st support members 32a is supported on the guide rail 44a so that reciprocation is possible along the 1st direction X1.

A guide rail 44b extending in the third direction Y1 is fixed to the second support portion 33b of the first support member 32a, or is formed integrally with the second support portion. A second linear slider 41a is attached to the first crank connecting member 34a and extends in the third direction Y1. The second linear slider 41a is supported and guided by the guide rail 44b so as to reciprocate. Accordingly, only one end portion of the first crank connecting member 34a is supported by the first support member 32a so as to be reciprocally movable along the third direction Y1.
The first and second linear sliders 40a and 41a may incorporate ball bearings that are in rolling contact with the guide rails 44a and 45a, respectively.

  The first crank connecting member 34a is formed, for example, in an arc block shape and has a through hole 46 having a circular cross section. The first crank connecting member 34a is a split surface 53 including the center of the through hole 46, and is formed so as to be split into a first half portion 51a and a second half portion 51b, and the second half portion 51b is a first half portion. It is fixed to 51a with screws or the like. The aforementioned second linear slider 41a is fixed to the flat portion of the first half portion 51a.

  The crank pin 16a of the first crankshaft 12a is rotatably inserted into the through hole 46 of the first crank connecting member 34a via a bearing such as a ball bearing or a plain bearing. Accordingly, the first crank connecting member 34a engages with the first crankshaft 12a, and connects the first crankshaft 12a and the first support member 32a.

  The connecting member has a first connecting rod 36a. One end of the first connecting rod 36a in the axial direction is connected to the first piston 24a via a support pin, and the other end in the axial direction is connected to the second support portion 33b of the first support member 32a. The first connecting rod 36a extends in the first direction X1 and is provided coaxially with the moving shaft of the first piston 24a. The first connecting rod 36a reciprocates integrally with the first support member 32a along the first direction X1, and reciprocates the first piston 24a along the first direction X1.

  As shown in FIG. 1, the second crankshaft 12b and the second XY separation crank mechanism 30b of the second drive unit 20b have the same configuration as the first crankshaft 12a and the first XY separation crank mechanism 30a of the first drive unit 20a, respectively. have. The second crankshaft 12b and the second XY separation crank mechanism 30b are arranged symmetrically with the first crankshaft 12a and the first XY separation crank mechanism 30a with respect to the center reference plane CRP.

  Specifically, the second crankshaft 12b is rotatably supported at both axial ends by bearings (not shown), and is disposed substantially parallel to the first crankshaft 12a. A set of crank webs 14b is fixed in the middle of the second crankshaft 12b, and a crank pin 16b (see FIG. 3) is fixed between the crank webs 14b. The crankpin 16b rotates eccentrically around the second crankshaft 12b according to the rotation of the second crankshaft 12b.

  The second XY separation crank mechanism 30b is a second support member (not shown) that can be reciprocated along the second direction X2 on the second installation plane MP2 including the central axis (movement axis, X axis) of the second piston 24b. L-type combinator) 32b and a second crank connection attached to the second support member 32b so as to reciprocate along a fourth direction Y2 (Y-axis direction) orthogonal to the second direction X2 in the second installation plane MP2. A member (crank connection plate) 34b and a second connecting rod 36b as a connecting member for connecting the second piston 24b and the second support member 32b are provided. The movement center axis of the second support member 32b (second direction X2), the movement center axis of the second crank connecting member 34b (fourth direction Y2), and the center movement axis of the second connecting rod 36b (second direction X2) are as follows. , Located on the second installation plane MP2.

  The second support member 32b is formed, for example, in an L shape, and extends in the second direction X2, and extends in the fourth direction Y2 from one end (here, the right end) of the first support portion 35a. 2 support part 35b. The first support portion 35a is fixed to the first linear slider 41a, and the first linear slider 41a is supported and guided by the guide rail 45a so as to be capable of reciprocating along the second direction X2. Thereby, only the 1st support part 35a among the 2nd support members 32b is supported on the guide rail 45a so that reciprocation is possible along the 2nd direction X2. In the present embodiment, the guide rail 45a is configured by a guide rail common to the guide rail 44a of the first drive unit 20a. The guide rail 45a may be separated from the guide rail 44a at the position of the center reference plane CRP.

A guide rail 45b extending in the fourth direction Y2 is fixed to the second support portion 35b of the second support member 32b, or is formed integrally with the second support portion. A second linear slider 41b is attached to the second crank connecting member 34b and extends in the fourth direction Y2. The second linear slider 41b is supported and guided by the guide rail 45b so as to reciprocate. Accordingly, only one end of the second crank connecting member 34b is supported by the second support member 32b so as to be reciprocally movable along the fourth direction Y2.
The second crank connecting member 34b has a through hole with a circular cross section, and the crank pin 16b of the second crank shaft 12b is rotatably inserted into the through hole through a bearing such as a ball bearing or a plain bearing. ing. Thereby, the second crank connecting member 34b engages with the second crankshaft 12b, and connects the second crankshaft 12b and the second support member 32b.

  One end of the second connecting rod 36b in the axial direction is connected to the second piston 24b via a support pin, and the other end in the axial direction is connected to the second support portion 35b of the second support member 32b. The second connecting rod 36b extends in the second direction X2 and is provided coaxially with the moving shaft of the second piston 24b. The second connecting rod 36b reciprocates integrally with the second support member 32b along the second direction X2, and reciprocates the second piston 24b along the second direction X2.

  As shown in FIGS. 1 and 2, the coupling synchronization mechanism 50 of the driving device 10 includes a first gear 52a coaxially attached to one end of the first crankshaft 12a and one end of the second crankshaft 12b. And a second gear 52b attached coaxially. The first gear 52a and the second gear 52b are formed to have the same diameter and the same number of teeth, and mesh with each other. The first crankshaft 12a and the second crankshaft 12b are connected to each other via a first gear 52a and a second gear 52b. When the first gear 52a rotates, the second gear 52b rotates in the opposite direction to the first gear 52a in synchronization with the rotation of the first gear 52a. Thereby, the 1st crankshaft 12a and the 2nd crankshaft 12b rotate in the mutually opposite direction synchronously.

  Since the first drive unit 20a and the second drive unit 20b are arranged and configured symmetrically with respect to the center reference plane CRP, the operation is also symmetric. As shown in FIG. 3, when the first piston 24a moves to the top dead center, the second piston 24b also moves to the top dead center in synchronization with this. As shown in FIG. 4, when the first piston 24a moves from the top dead center toward the bottom dead center, the second piston 24b moves simultaneously from the top dead center toward the bottom dead center. As shown in FIGS. 3 and 4, the first XY separation crank mechanism 30 a and the second XY separation crank mechanism 30 b also operate in synchronization with each other while maintaining a symmetric state with respect to the center reference plane CRP.

  When the drive device 10 configured as described above is used as an engine, an intake valve and an exhaust valve are provided on the cylinder head of the first cylinder 22a and the cylinder head of the second cylinder 22b, and the first cylinder 22a and the second cylinder 22b are provided. Fuel and air are introduced into the interior, and after being compressed by the first piston 24a and the second piston 24b, the fuel is combusted. Accordingly, driving force is input to the first piston 24a and the second piston 24b, and the first piston 24a and the second piston 24b reciprocate along the first direction X1 and the second direction X2, respectively. The reciprocating motion of the first piston 24a is converted into a rotational motion by the reciprocating motion of the first support member 32a in the first direction X1 and the reciprocating motion of the first crank connecting member 34a in the third direction Y1 in the first XY separation crank mechanism 30a. , Transmitted to the first crankshaft 12a. Thereby, a rotation output is given to the 1st crankshaft 12a.

  At the same time, the reciprocating motion of the second piston 24b is turned into the rotational motion by the reciprocating motion of the second support member 32b in the second direction X2 and the reciprocating motion of the second crank connecting member 34b in the fourth direction Y2 in the second XY separation crank mechanism 30b. It is converted and transmitted to the second crankshaft 12b. Thereby, a rotation output is given to the second crankshaft 12b.

  When the drive device 10 is used as a compressor, a rotational force is input to at least one of the first crankshaft 12a and the second crankshaft 12b by a motor or the like. As a result, the first crankshaft 12a and the second crankshaft 12b rotate in directions opposite to each other, and the crankpin of each crankshaft rotates eccentrically around the crankshaft. The eccentric rotational movement of the crank pin 16a of the first crankshaft 12a is caused by the reciprocating movement in the third direction Y1 and the first direction X1 by the first crank connecting member 34a and the first support member 32a of the first XY separation crank mechanism 30a. The reciprocating motion is separated into the reciprocating motion, and the reciprocating motion in the first direction X1 of the first support member 32a is transmitted to the first piston 24a via the first connecting member 36a. Thus, the first piston 24a reciprocates along the first direction X1 in the first cylinder 22a, compresses the fluid in the first cylinder 22a, and then outputs it from the cylinder head.

  Similarly, the eccentric rotational motion of the crank pin 16b of the second crankshaft 12b is the same as the reciprocating motion in the fourth direction Y2 by the second crank connecting member 34b and the second support member 32b of the second XY separation crank mechanism 30b. The reciprocating motion in the direction X2 is separated, and the reciprocating motion in the second direction X2 of the second support member 32b is transmitted to the second piston 24b via the second connecting member 36b. Thereby, the second piston 24b reciprocates along the second direction X2 in the second cylinder 22b, compresses the fluid in the second cylinder 22b, and then outputs it from the cylinder head.

  According to the drive device 10 configured as described above, in the first drive unit 20a and the second drive unit 20b, the first and second XY separation crank mechanisms 30a and 30b cause the rotational motion and the first motion of the first crankshaft 12a. 2 Rotating motion of the crankshaft 12b is separated and converted into linear reciprocating motion in the first direction and linear reciprocating motion in the third direction and the fourth direction orthogonal to the first direction and the second direction, respectively. And complete parallel movement of the first piston 24a and the second piston 24b can be realized. Therefore, it is possible to eliminate the contact of the piston with the cylinder, to improve the sealing performance, to reduce the friction loss, and to achieve high efficiency with no side thrust loss. In addition, the first drive unit and the second drive unit are arranged symmetrically with respect to the central reference plane and symmetrically in the front-rear direction (mirror arrangement). A structure can be constructed.

  Conventionally, the vibration is finally reduced by increasing the number of cylinders such as 6 cylinders, 8 cylinders, and 12 cylinders. However, when the engine is configured by the drive device according to this embodiment, the engine is completely balanced by 2 cylinders, It is possible to achieve vibration-free operation compared to conventional multi-cylinder engines. Further, when the drive device 10 is used as an engine, it is possible to obtain the same reverse rotation output that is mutually reversed from the first crankshaft and the second crankshaft, that is, the same synchronous reverse rotation biaxial output. With this synchronous, same-reversing two-axis output, for example, helicopter wings and ship screws can be driven to generate stable thrust without blurring. Furthermore, the drive device 10 can be used for an airplane engine. Since the first piston and the second piston simultaneously move in opposite directions, the drive device 10 can be operated without vibration even when applied to a compressor and a pump as well as the engine.

Further, since there is no side thrust of the piston by the XY separation crank mechanism, it becomes possible to form the cylinder and the piston with ceramic, glass, etc., and it is possible to construct a low temperature and heat retention type engine with high thermal efficiency. Furthermore, since the drive device is not vibrated by side thrust, the cylinder can be formed of carbon fiber or a plastic material such as PBT. This makes it possible to produce an ultralight engine that is 1/5 to 1/10 that of a conventional engine.
As described above, according to the first embodiment, it is possible to obtain a drive device that reduces friction loss and vibration and has high operating efficiency.
FIG. 26 is a diagram showing a comparison between a displacement formula of a slider crank mechanism having a conventional connecting rod and a displacement formula of an XY separation crank mechanism according to this embodiment, and FIG. 27 is an XY separation crank mechanism according to this embodiment. FIG. 28 is a diagram illustrating a dynamic analysis formula of the conventional slider crank mechanism, and FIG. 29 is a conventional slider crank mechanism and an XY separation crank mechanism according to the present embodiment. It is a figure which compares and shows a vibration analysis result about.

  As shown in FIG. 26, in the conventional slider crank mechanism, the stroke formula has a square term and a square root term, and if the stroke is differentiated by time dt, it circulates and diverges, so it can be seen that vibration does not disappear. . On the other hand, in the XY separation crank mechanism according to the present embodiment, S1 and S2 are linear expressions and do not diverge even if differentiated by dt. Therefore, it can be seen that vibration is always eliminated by arranging the first drive unit and the second drive unit each having an XY separation crank mechanism as a mirror.

  As shown in FIGS. 27 to 29, as shown in dynamic analysis equations (3) and (4) of the conventional slider crank mechanism, the slider crank mechanism generates a phase deviation due to the rotational speed and uniquely stops vibration. Will be difficult. On the other hand, as shown in dynamic analysis equations (1) and (2) of the XY separation crank mechanism, since the XY separation crank mechanism is a primary expression of only -mg, the first drive unit and the second drive unit By arranging the mirrors, vibration can be easily canceled.

  Next, drive devices according to other embodiments will be described. In other embodiments described below, the same parts as those in the first embodiment described above are denoted by the same reference numerals, and detailed description thereof is omitted, and the parts different from those in the first embodiment. Will be described in detail.

(Second Embodiment)
FIG. 5 is a perspective view showing a driving apparatus according to the second embodiment. According to the second embodiment, as the first piston 24a and the second piston 24b, pistons having a different planar shape and cross-sectional shape, that is, non-circular shapes are used. In the present embodiment, the first piston 24a and the second piston 24b are formed in an oval shape including an oval shape and an oval shape, and have a major axis L and a minor axis S orthogonal to the major axis. The first cylinder 22a and the second cylinder 22b have an oval cross-sectional shape corresponding to the first piston 24a and the second piston 24b, respectively.

The long axis L of the first piston 24a is located in the first installation plane, and is located in parallel with the second support portion 33b of the first support member 32a, that is, in parallel with the third direction Y1. The long axis L of the second piston 24b is located in the second installation plane, and is located in parallel with the second support portion 35b of the second support member 32b, that is, in parallel with the fourth direction Y2.
The other configuration of the drive device 10 is the same as that of the drive device according to the first embodiment.

  When the oval first and second pistons 24a and 24b are used, the displacement of the piston can be doubled or tripled compared to a circular piston having the same diameter as the short axis S of the piston. Further, since the piston area can be increased with the same stroke, the volume is also increased. By making the circular piston into an oval piston, for example, the capacity becomes 2.5 times. Therefore, while constituting a 2000 cc engine with two cylinders, the weight is about ¼ that of a conventional circular piston, four-cylinder engine, and the weight and size can be reduced.

Further, in the driving device 10, complete parallel movement of the first piston 24a and the second piston 24b can be realized. Therefore, even when a non-circular piston, for example, an oval piston is used, or when a large piston is used, the piston does not come into contact with each other, sealing performance is good, and high efficiency can be obtained without side thrust loss.
In addition, the drive device 10 according to the second embodiment can obtain the same effects as the drive device according to the first embodiment. In the second embodiment, the shape of the piston is not limited to the oval shape, and other non-circular shapes such as a rectangular shape with rounded corners, other polygonal shapes, and a constricted elliptical shape at the center. Etc.

(Third embodiment)
FIG. 6 is a perspective view showing a driving apparatus according to the third embodiment. In the third embodiment, the configuration of the connection synchronization mechanism is different from that of the first embodiment. As shown in FIG. 6, the connection synchronization mechanism 50 is coaxially attached to one end of the first crankshaft 12a and the first drive pulley 54a coaxially attached to one end of the first crankshaft 12a. It is stretched over the second drive pulley 54b, a plurality of tension pulleys 56a, 56b, 56c each having a rotation axis parallel to the rotation axis of these drive pulleys, the first and second drive pulleys, and the plurality of tension pulleys. And an endless toothed belt 58.

  The first crankshaft 12a and the second crankshaft 12b are connected to each other via a connection synchronization mechanism 50, and rotate in directions opposite to each other in synchronization. That is, when the first drive pulley 54a rotates together with the first crankshaft 12a, the rotation of the first drive pulley 54a is transmitted to the second drive pulley 54b by the toothed belt 58, and the second drive pulley 54b is transmitted to the second crankshaft. It rotates in the reverse direction together with 12b. Thereby, the 1st crankshaft 12a and the 2nd crankshaft 12b rotate in the mutually opposite direction synchronously.

  Also in the third embodiment, as the first piston 24a and the second piston 24b, pistons that are irregular in plane shape and cross-sectional shape, that is, non-circular, for example, oval pistons, are used.

  In the third embodiment, the other configuration of the driving apparatus 10 is the same as that of the driving apparatus according to the first embodiment or the second embodiment. The drive device 10 according to the third embodiment can obtain the same operational effects as the drive device according to the first embodiment. In the third embodiment, the connection synchronization mechanism 50 is not limited to a combination of a pulley and a belt, and may be configured by a combination of a sprocket and a chain.

(Fourth embodiment)
FIG. 7 is a perspective view showing a driving apparatus according to the fourth embodiment. In the fourth embodiment, the drive device 10 is multi-cylinder, and is configured as, for example, a 4-cylinder drive device. That is, the drive device 10 includes a third drive unit 20c and a fourth drive unit 20d in addition to the first drive unit 20a and the second drive unit 20b described above. The third drive unit 20c has the same configuration as the first drive unit 20a, and is arranged side by side in a direction parallel to the first drive unit 20a and the center reference plane CRP. The fourth drive unit 20d has the same configuration as the second drive unit 20b, and is arranged side by side in a direction parallel to the second drive unit 20b and the center reference plane CRP.

  The third drive unit 20c and the fourth drive unit 20d have the same configuration. The third drive unit 20c and the fourth drive unit 20d are arranged on both sides of the center reference plane CRP, respectively, and the third drive unit 20c and the fourth drive unit 20d are left and right, front and rear with respect to the center reference plane CRP. They are arranged symmetrically (mirror arrangement) and configured.

  The third drive unit 20b is located on one side of the center reference plane CRP and has a third cylinder 22c provided on a third installation plane MP3 orthogonal to the center reference plane CRP, and in the first direction X1 within the third installation plane MP3. A third piston 24c provided in the third cylinder 22c so as to freely reciprocate along, a first crankshaft 12a extending perpendicular to the third installation plane MP3, and a third piston 24c in the third installation plane MP3. A third XY separation crank mechanism 30c is provided between the first crankshaft 12a and converts the reciprocating motion of the third piston 24a and the rotational motion of the first crankshaft 12a to each other. The third installation plane MP3 faces the first installation plane MP1 of the first drive unit 20a in parallel. The first direction that is the reciprocating direction of the third piston 24c is a first direction X1 that is orthogonal to the center reference plane CRP. Further, the first crankshaft 12a is connected to the first crankshaft 12a of the first drive unit 20a or is integrally formed and extends coaxially with each other.

  The fourth drive unit 20d is located on the opposite side of the center reference plane CRP and has a fourth cylinder 22d provided on the fourth installation plane MP4 orthogonal to the center reference plane CRP, and the second direction X2 in the fourth installation plane MP4. A fourth piston 24d provided in the fourth cylinder 22d so as to be capable of reciprocating along, a second crankshaft 12b extending orthogonally to the fourth installation plane MP4, and a fourth piston 24d in the fourth installation plane MP4. And a second XY separation crank mechanism 30d for converting the reciprocating motion of the fourth piston 24d and the rotational motion of the second crankshaft 12b to each other.

  The fourth installation plane MP4 is located symmetrically with the third installation plane MP3 with respect to the center reference plane CRP. Further, the fourth installation plane MP4 faces the second installation plane MP2 of the second drive unit 20b in parallel. The second direction that is the reciprocating direction of the fourth piston 24d is a direction that is symmetric to the first direction X1 described above, and is a second direction X2 that is orthogonal to the center reference plane CRP. The first direction X1 and the second direction X2 form an angle of 180 degrees, that is, the same direction, and the third piston 24c and the fourth piston 24d are arranged coaxially with each other. Further, the second crankshaft 12b of the fourth drive unit 20d is connected to the second crankshaft 12b of the second drive unit 20b or is integrally formed and extends coaxially with each other.

  The third XY separation crank mechanism 30c includes a third support member (L-shaped combinator) 32c provided so as to freely reciprocate along the first direction X1, and a third installation plane MP3 that is orthogonal to the first direction X1. A third crank connecting member (crank connecting plate) which is attached to the third support member 32c so as to be reciprocally movable along the direction Y1 (Y-axis direction) and is rotatably engaged with a crank pin of the first crank shaft 12a. 34c and a connecting rod 36c that connects the third piston 24c and the third support member 32c.

  The third support member 32c is formed in an L shape and extends in the first direction X1, and a second support portion extends from one end (here, the left end) of the first support portion in the third direction Y1. Is integrated. Of the third support member 32c, only the first support portion is supported on the guide rail 44a via the first linear slider so as to be capable of reciprocating along the first direction X1. Only one end of the third crank connecting member 34c is supported by the third support member 32c so as to be reciprocally movable along the third direction Y1.

  The fourth XY separation crank mechanism 30d of the fourth drive unit 20d has the same configuration as the third XY separation crank mechanism 30c, and is arranged symmetrically with the third XY separation crank mechanism 30c with respect to the center reference plane CRP. That is, the fourth XY separation crank mechanism 30d is orthogonal to the second direction X2 in the fourth support member (L-shaped combinator) 32d provided to be reciprocally movable along the second direction X2 and the fourth installation plane MP4. A fourth crank connection member (crank connection) is attached to the fourth support member 32d so as to be reciprocally movable along the fourth direction Y2 (Y-axis direction) and is rotatably engaged with the crank pin of the second crankshaft 12b. Plate) 34d and a connecting rod 36d for connecting the fourth piston 24d and the fourth support member 32d.

  In the fourth embodiment, as the first, second, third, and fourth pistons 24a, 24b, 24c, and 24d, the planar shape and the cross-sectional shape are irregular, that is, pistons that are non-circular, for example, long An oval piston having an axis L and a short axis S is used. The first piston 24a is arranged so that its long axis L is parallel to the third direction Y1, and the second piston 24b is arranged so that its long axis L is parallel to the fourth direction Y2. Similarly, the third piston 24c is arranged so that its long axis L is parallel to the third direction Y1, and the second piston 24b is arranged so that its long axis L is parallel to the fourth direction Y2. ing. Accordingly, the long axis L of the third piston 24c is aligned in parallel with the long axis L of the first piston 24a, and the long axis L of the fourth piston 24d is aligned in parallel with the long axis L of the second piston 24b.

  In the fourth embodiment, the other configuration of the driving apparatus 10 is the same as that of the driving apparatus according to the first embodiment or the second embodiment. The drive device 10 according to the fourth embodiment can obtain the same functions and effects as those of the drive device according to the first embodiment. Further, the drive device 10 can be easily multi-cylindered. According to this embodiment, a so-called horizontally opposed four-cylinder engine or compressor can be provided. Further, by using an oval-shaped piston and arranging the plurality of pistons so that the long axes of the pistons are arranged in parallel, the plurality of pistons can be arranged close to each other along the axial direction of the crankshaft. Thereby, even when the number of cylinders of the drive device is increased, the size of the drive device along the axial direction of the crankshaft can be shortened, and the drive device can be reduced in size.

  In the fourth embodiment, the driving device is not limited to four cylinders, and may be six cylinders or eight cylinders or more. Further, the piston of each drive unit is not limited to the oval shape, and other different or circular pistons may be used.

(Fifth embodiment)
FIG. 8 is a side view showing the driving apparatus according to the fifth embodiment. In the first to fourth embodiments described above, the first direction that is the moving direction of the first piston and the second direction that is the moving direction of the second piston are 180 degrees opposite to each other, that is, coaxial. 1 shows a so-called horizontally-opposed drive device that extends in a horizontal direction. On the other hand, according to the fifth embodiment, the drive device 10 includes the first drive unit 20a and the second drive unit 20b disposed on both sides of the center reference plane CRP, respectively. The second drive unit 20b has an angle θ smaller than 180 degrees between the first direction X1 that is the moving direction of the first piston 24a and the second direction X2 that is the moving direction of the second piston 24b, for example, 60 to 90 degrees. It is arranged to form.

  The first drive unit 20a and the second drive unit 20b are the same as the first drive unit and the second drive unit in the first embodiment, respectively. However, in the fifth embodiment, oval pistons are used as the first piston 24a and the second piston 24b.

  The first drive unit 20a is provided on a first installation plane MP1 that is located on one side of the center reference plane CRP and orthogonal to the center reference plane CRP. The first piston 24a is provided in the first cylinder 22a so as to be reciprocally movable along the first direction X1 in the first installation plane MP1. In the present embodiment, the first direction X1 is a direction that intersects the center reference plane CRP at an angle smaller than 90 degrees. The first crankshaft 12a is disposed substantially parallel to the center reference plane CRP. The long axis L of the first piston 24a is arranged in a direction orthogonal to the first direction X1 in the first installation plane MP1.

  The second drive unit 20b is provided on the second installation plane MP2 that is located on the opposite side of the center reference plane CRP and orthogonal to the center reference plane CRP. The second installation plane MP2 is located symmetrically with the first installation plane MP1 with respect to the center reference plane CRP. Thus, the second drive unit 20b is arranged symmetrically (mirror arrangement) with respect to the first drive unit 20a with respect to the center reference plane CRP. The second direction X2, which is the reciprocating direction of the second piston 24b, is a symmetric direction with respect to the first direction X1 of the first piston 24a, and intersects the center reference plane CRP at an angle smaller than 90 degrees. The first direction X1 and the second direction X2 intersect each other on the center reference plane CRP and form an angle θ smaller than 180 degrees, for example, 50 to 120 degrees. The long axis L of the second piston 24b is arranged in a direction orthogonal to the second direction X2 in the second installation plane MP2.

In addition, when the first direction X1 and the second direction X2 form an angle θ of 10 to 170 degrees, the first crankshaft 12a of the first crankshaft 12a is balanced in order to balance the rotation of the first and second crankshafts 12a and 12b. Notches 15a and 15b for balance adjustment are provided on the crank web 14a and the crank web 14b of the second crankshaft 12b.
Other configurations of the driving device 10 are the same as those of the driving device according to the first embodiment.

  As described above, the driving apparatus 10 according to the fourth embodiment can constitute a so-called V-type engine. Also in the driving device 10 according to the fifth embodiment, the same operational effects as those of the driving device according to the first embodiment described above can be obtained.

(Sixth embodiment)
FIG. 9 is a side view showing a driving apparatus according to the sixth embodiment. The drive device 10 according to the present embodiment is configured substantially the same as the drive device 10 according to the fifth embodiment described above. In the sixth embodiment, as the first piston 24a and the second piston 24b, pistons having a planar shape and a circular cross-sectional shape are used.

  In the first drive unit 20a, the first support member 32a of the first XY separation crank mechanism 30a is provided in the opposite direction to the first support member in the above-described embodiment. That is, the first support portion 33a and the guide rail 44a of the first support member 32a are disposed on the center reference plane CRP side with respect to the first crankshaft 12a in the first installation plane MP1, and are parallel to the first direction X1. It extends. The second support portion 33b of the first support member 32a extends in the third direction Y1 from one end of the first support portion 33a and is orthogonal to the moving axis (first direction X1) of the first piston 24a.

  In the second drive unit 20b arranged and configured symmetrically with the first drive unit 20a, the first support part 35a and the guide rail 45a of the second XY separation crank mechanism 30b are arranged on the second crankshaft 12b on the second installation plane MP2. Is disposed on the center reference plane CRP side and extends in parallel with the second direction X2. The second support portion 35b of the second support member 32b extends from one end of the second support portion 33b in the fourth direction Y2, and is orthogonal to the movement axis (second direction X2) of the second piston 24b.

  The first direction X1 that is the moving direction of the first piston 24a and the second direction X2 that is the moving direction of the second piston 24b intersect with each other in the center reference plane CRP, and an angle θ smaller than 180 degrees For example, 60 to 90 degrees.

  Also in the sixth embodiment configured as described above, a so-called V-type driving device 10 can be configured. In addition, also in the sixth embodiment, the same operational effects as those in the first embodiment or the fifth embodiment can be obtained.

(Seventh embodiment)
FIG. 10 is a side view showing a driving apparatus according to the seventh embodiment. According to this embodiment, the 1st drive unit 20a and the 2nd drive unit 20b of the drive device 10 are the 1st direction X1 which is the moving direction of the 1st piston 24a, and the 2nd direction which is the moving direction of the 2nd piston 24b. X2 is arranged symmetrically so as to be parallel to each other and so as to be parallel to the center reference plane CRP. Thereby, the first support portion 33a and the guide rail 44a of the first XY separation crank mechanism 30a, and the first support portion 35a and the guide rail 45a of the second XY separation crank mechanism 30b are parallel to each other and the center reference plane CRP. It extends in parallel. The other structure of the drive device 10 is the same as that of the drive device according to the fifth embodiment shown in FIG.

(Eighth embodiment)
FIG. 11 is a side view showing the driving apparatus according to the eighth embodiment. According to the present embodiment, as in the seventh embodiment described above, the first drive unit 20a and the second drive unit 20b of the drive device 10 are connected to the first direction X1 that is the moving direction of the first piston 24a and the first direction X1. The two pistons 24b are arranged symmetrically so that the second direction X2 that is the moving direction of the two pistons 24b is parallel to each other and parallel to the center reference plane CRP.

  In the first drive unit 20a, the first support member 32a of the first XY separation crank mechanism 30a is provided in the opposite direction to the first support member in the above-described embodiment. That is, the first support portion 33a and the guide rail 44a of the first support member 32a are disposed on the center reference plane CRP side with respect to the first crankshaft 12a in the first installation plane MP1, and are parallel to the first direction X1. It extends. The second support portion 33b of the first support member 32a extends in the third direction Y1 from one end of the first support portion 33a and is orthogonal to the moving axis (first direction X1) of the first piston 24a.

  In the second drive unit 20b, the first support portion 35a and the guide rail 45a of the second XY separation crank mechanism 30b are disposed on the center reference plane CRP side with respect to the second crankshaft 12b in the second installation plane MP2, It extends in parallel with the two directions X2. The second support portion 35b of the second support member 32b extends from one end of the second support portion 33b in the fourth direction Y2, and is orthogonal to the movement axis (second direction X2) of the second piston 24b.

  Other configurations of the driving device 10 are the same as those of the driving device according to the seventh embodiment.

(Ninth embodiment)
FIG. 12 is a side view showing a driving apparatus according to the ninth embodiment. According to the present embodiment, as in the seventh embodiment described above, the first drive unit 20a and the second drive unit 20b of the drive device 10 are connected to the first direction X1 that is the moving direction of the first piston 24a and the first direction X1. The two pistons 24b are arranged symmetrically so that the second direction X2 that is the moving direction of the two pistons 24b is parallel to each other and parallel to the center reference plane CRP. In the present embodiment, as the first piston 24a and the second piston 24b, pistons having a planar shape and a circular cross-sectional shape are used. Other configurations of the driving device 10 are the same as those of the driving device according to the seventh embodiment.

  According to the seventh to ninth embodiments described above, the parallel type driving device 10 can be provided. In addition, in the seventh to ninth embodiments, the same operational effects as those of the first embodiment described above can be obtained.

  The V-type drive devices according to the fifth and sixth embodiments described above and the parallel-type drive devices according to the seventh to ninth embodiments are not limited to two cylinders. Multiple cylinders such as cylinders, 6 cylinders, or 8 cylinders or more may be used.

  In the embodiment described above, the first installation plane MP1 and the second installation plane MP2 on which the first drive unit and the second drive unit are arranged are planes orthogonal to the center reference plane CRP, but are not limited to this. It may be a plane that intersects the central reference plane CRP at an angle that is larger or smaller than the angle. In this case, the first crankshaft and the second crankshaft are not parallel to the center reference plane CRP and are inclined with respect to the center reference plane CRP. However, for example, by using a bevel gear as a connection synchronization mechanism The first crankshaft and the second crankshaft can be connected to each other, and the same reverse rotation output can be obtained which are mutually reversed.

(Tenth embodiment)
FIG. 13 is a perspective view showing a driving apparatus according to the tenth embodiment, and FIG. 14 is an exploded perspective view of an XY separation crank mechanism. In the tenth embodiment, the configuration of the XY separation crank mechanism is different from that of the first embodiment.

  As shown in FIG. 13, the drive device 10 includes a first drive unit 20a having a first crankshaft 12a, a second drive unit 20b having a second crankshaft 12b, a first crankshaft 12a, and a second crankshaft. 12b, and a connection synchronization mechanism 50 that rotates the first crankshaft and the second crankshaft in synchronization with each other.

  The first drive unit 20a and the second drive unit 20b have the same configuration. The first drive unit 20a and the second drive unit 20b are respectively disposed on both sides of the center reference plane CRP, and further, the first drive unit 20a and the second drive unit 20b are left and right, front and rear with respect to the center reference plane CRP. They are arranged symmetrically (mirror arrangement) and configured. The first drive unit 20a is provided on the first installation plane MP1 positioned on one side of the center reference plane CRP and orthogonal to the center reference plane CRP, and the second drive unit 20b is positioned on the opposite side of the center reference plane CRP and centered. It is provided on a second installation plane MP2 that is orthogonal to the reference plane CRP, that is, a second installation plane MP2 that is symmetrical to the first installation plane MP1.

  The first drive unit 20a is provided between the first piston 24a and the first crankshaft 12a in the first installation plane MP1 and the first crankshaft 12a extending orthogonally to the first installation plane MP1. A first XY separation crank mechanism 30a that mutually converts the reciprocating motion of the piston 24a and the rotational motion of the first crankshaft 12a. A first direction that is a reciprocating direction of the first piston 24a is a first direction X1 orthogonal to the center reference plane CRP. The first crankshaft 12a is disposed substantially parallel to the center reference plane CRP.

  The second drive unit 20b is provided between the second piston 24b and the second crankshaft 12b in the second installation plane MP2, and between the second crankshaft 12b extending perpendicularly to the second installation plane MP2, A second XY separation crank mechanism 30b that mutually converts the reciprocating motion of the piston 24b and the rotational motion of the second crankshaft 12b. The second direction, which is the reciprocating direction of the second piston 24a, is a direction symmetric to the first direction X1 described above, and is a second direction X2 orthogonal to the center reference plane CRP. The first direction X1 and the second direction X2 form an angle of 180 degrees, that is, the same direction, and the first piston 24a and the second piston 24b are arranged coaxially with each other.

  The first XY separation crank mechanism 30a and the second XY separation crank mechanism 30b have the same configuration and are arranged symmetrically with respect to the center reference plane CRP in the left-right direction. The second XY separation crank mechanism 30b will be described in detail as a representative. As shown in FIGS. 13 and 14, the second XY separation crank mechanism 30b reciprocates along the second direction X2 on the second installation plane MP2 including the central axis (movement axis, X axis) of the second piston 24b. A second support member (combinator) 32b provided freely and a second support member 32b reciprocally movable along a fourth direction Y2 (Y-axis direction) orthogonal to the second direction X2 on the second installation plane MP2. And a second connecting rod 36b as a connecting member for connecting the second piston 24b and the second support member 32b. The movement center axis of the second support member 32b (second direction X2), the movement center axis of the second crank connecting member 34b (fourth direction Y2), and the center movement axis of the second connecting rod 36b (second direction X2) are as follows. , Located on the second installation plane MP2.

  In the present embodiment, the second support member 32b is formed in a rectangular frame shape, for example. That is, the second support member 32b includes a first support portion 35a extending in the second direction X2, and a second support portion 35b and a third support portion 35c extending in the fourth direction Y2 from both axial ends of the first support portion 35a. Is integrated. In the present embodiment, the second support member 32b connects the extended end of the second support portion 35b and the extended end of the third support portion 35c, and faces the first support portion 35a with a gap therebetween. The support part 35d is provided integrally. The mutually opposing inner surfaces of the second support part 35b and the third support part 35c are formed flat and parallel to each other and extend along the fourth direction Y2. The second support member 32b is die-cast, for example, with aluminum.

  The first linear slider 41a is fixed to the first support portion 35a. Further, the second guide rail 45a is installed on the inner surface of the casing (not shown), and extends in the second direction X2 within the second installation plane MP2. The first linear slider 41a is supported and guided by the second guide rail 45a so as to be reciprocally movable. Thereby, only the 1st support part 35a is supported on the 2nd guide rail 45a so that reciprocation is possible along the 2nd direction X2 among the 2nd support members 32b. The second linear slider 41a may incorporate a ball bearing that is in rolling contact with the second guide rail 45a.

  The second crank connecting member 34b is configured as a rectangular block-shaped member. The left and right side surfaces of the crank connecting member 34b constitute a first sliding surface 60a and a second sliding surface 60b, respectively. The first sliding surface 60a and the second sliding surface 60b are each formed flat and parallel to each other, and extend along the fourth direction Y2.

  A circular through hole 46 is formed through substantially the center of the second crank connecting member 34b. The through hole 46 extends in the Z-axis direction orthogonal to the second direction X2 and the fourth direction Y2, that is, in a direction parallel to the second crankshaft 12b. The crank pin 16b of the second crankshaft 12b is rotatably inserted into the through hole 46. A plain bearing is formed on the sliding surface, that is, the inner surface of the through hole 46 by lining processing (plating) such as electroforming or electrodeposition. A wire cut may be used after plating.

  The second crank connecting member 34b is disposed in the frame-shaped second support member 32b, the first sliding surface 60a slidably contacts the inner surface of the second support portion 35b, and the second sliding surface 60b It is slidably in contact with the inner surface of the third support portion 35c. Thereby, the second crank connecting member 34b is supported and guided between the second and third support portions 35b and 35c of the second support member 32b so as to reciprocate along the fourth direction Y2. Further, the crank pin 16b of the second crankshaft 12b is rotatably inserted into the through hole 46 of the second crank connecting member 34b. Thus, the second crank connecting member 34b is engaged with the second crankshaft 12, and connects the second crankshaft 12b and the second support member 32b.

  Note that guide rails extending in the fourth direction Y2 are installed on the inner surfaces of the second support portion 35b and the third support portion 35c of the second support member 32b, respectively, and the first sliding surface 60a of the second crank connection member 34b. In addition, guide grooves that engage with the guide rails may be provided in the second sliding surface 60b.

  The second crank connecting member 34b is divided into two members (a first half portion 64a including a first sliding surface 60a, and a first half surface 64a, which are divided along a dividing surface 62 that passes through the central axis of the through hole 46 and is orthogonal to the second direction X2. The second half portion 64b including the second sliding surface 60b) is engaged, and the two members are engaged in a state where the divided surfaces 62 face each other, thereby forming a crank connecting member 34b having a rectangular block shape. Yes. The dividing surface 62 is a surface that passes through the central axis of the through hole 46 and extends in the fourth direction Y2. Further, the dividing surface 62 is formed in a corrugated surface having a wave shape, an S shape, or a cyclone shape. The unevenness of the dividing surface 62 is alternately arranged in the Z-axis direction (the axial direction of the through hole 46), and the respective recesses and protrusions extend in the fourth direction Y2. In the present embodiment, each divided surface 62 has arcuate concave surfaces and arcuate convex surfaces that are alternately arranged. In the engaged state, the gap between the dividing surface 61 of the first half portion 64a and the dividing surface 61 of the second half portion 64b is formed to be about 100 μm. The first and second half portions 64a and 64b are preferably formed of a material that easily contains lubricating oil, such as copper, brass, or fine ceramic. Further, the first and second half portions 64a and 64b can be made of engineering plastics such as ABS, and can be made by performing vapor deposition plating or the like on the surface.

  In addition, each division surface 62 of the 1st half part 64a and the 2nd half part 64b is good also as an uneven surface which has a 2 or more convex part and / or a 2 or more recessed part. In addition, the concave / convex surface only needs to have concave portions and convex portions arranged in the Z-axis direction, and the shapes of the concave portions and the convex portions themselves are not limited to curved surfaces but can be variously changed to other shapes.

  One end of the second connecting rod 36b of the second XY separation crank mechanism 30b is connected to the second piston 24b via a support pin, and the other end is connected to the second support portion 35b of the second support member 32b. The second connecting rod 36b extends in parallel with the second direction X2 and coaxially with the second piston 24b. The second connecting rod 36b reciprocates integrally with the second support member 32b along the second direction X2, and reciprocates the second piston 24b along the second direction X2. The connecting member is not limited to a single connecting rod, and a plurality of connecting rods or a plate-like connecting arm extending in the fourth direction Y2 may be used.

  When the drive device 10 is used as an engine, a driving force is input to the second piston 24b, and the second piston 24b reciprocates along the second direction X2. The reciprocating motion of the second piston 24b is converted into a rotational motion by the reciprocating motion of the second support member 32b in the second direction X2 and the reciprocating motion of the second crank connecting member 34b in the fourth direction Y2 in the second XY separation crank mechanism 30b. , Transmitted to the second crankshaft 12b. Thereby, a rotation output is given to the second crankshaft 12b.

  As shown in FIG. 13, the first XY separation crank mechanism 30a is configured similarly to the second XY separation crank mechanism 30b, and is a rectangular frame-shaped first support member 32a provided so as to be reciprocally movable along the first direction X1. And a block-shaped first crank connecting member 34a supported and guided in the first support member 32a so as to be reciprocally movable along the third direction Y1, and the first support member 32a and the first piston 24a are connected. A first connecting rod 36a. A crank pin of the first crankshaft 12a is rotatably inserted through the through hole of the first crank connecting member 34a.

The first XY separation crank mechanism 30a is arranged and configured symmetrically with the second XY separation crank mechanism 30b with respect to the center reference plane CRP, and operates symmetrically with the second XY separation crank mechanism 30b.
In the tenth embodiment, the other configuration of the driving device 10 is the same as that of the driving device according to the first embodiment or the second embodiment described above.

  The drive device 10 according to the tenth embodiment configured as described above can obtain the same effects as the drive device 10 according to the first embodiment. Furthermore, according to the tenth embodiment, the support member in the XY separation crank mechanism is formed in a rectangular frame shape, and the crank connecting member is slidably arranged in the XYZ directions in the frame body, whereby the linear guide is Omitted and the number of components of the XY separation crank mechanism can be reduced. Further, at the time of assembly, the crank connecting member is divided and mounted on the crankshaft, and after mounting, the crank connecting member is mounted between the second support portion and the third support portion of the support member. Thereby, a crank connection member can be assembled | attached with respect to the crankshaft 40 which has a crankpin. As a result, the number of man-hours for assembling the crank mechanism can be reduced, and even in the case of multiple cylinders, the assembly can be facilitated and the assemblability can be improved. Furthermore, the support member and the crank connecting member can have a function of automatically adjusting the sliding at the optimum position.

  The crank connecting member is divided into two on the left and right sides of the central axis of the through hole 46, and the dividing surface 62 is formed in an uneven shape so that there is an opening in the XY direction between the divided first half portion 64a and second half portion 64b. However, inconvenience due to mutual interference can be prevented. When the uneven shape is a wave shape, an S shape, or a cycloid shape, mutual interference between the two members can be removed even in the ZY plane perpendicular to the Z-axis direction. By forming the clearance between the two members with a small gap of about 100 μm, for example, it is possible to insulate a three-dimensional force between the XY plane and the ZY plane.

  FIG. 15 shows the crank when the crank connecting member is divided into two parts by the uneven dividing surface (a) and the crank connecting member is an undivided integral part (b) as in this embodiment. The stress acting on the connecting member is shown in comparison. As shown in FIG. 15 (a), in the crank connecting member according to the present embodiment, even when a stress is applied to the sliding surface of one half portion, the stress is insulated at the dividing surface, and the other half portion is insulated. The deformation of the other half is not seen. Therefore, there is no side thrust between the crank connecting member and the support member, and a smooth sliding operation of the XY separation crank mechanism can be realized.

  On the other hand, as shown in FIG. 15B, when the crank connecting member is integrated, when the stress acts on one sliding surface, the crank connecting member is deformed as a whole. Therefore, an opposing flat surface is easily formed between the sliding surface of the crank connection member and the sliding surface of the support member, and a side thrust is generated between these sliding surfaces.

(Eleventh embodiment)
FIG. 16 is a perspective view showing the drive device according to the eleventh embodiment, FIG. 17 is a perspective view of the drive device viewed from the side opposite to FIG. 16, and FIG. 18 is a partially cutaway view of the drive device. It is a front view. According to the present embodiment, the drive device constitutes a two-axis pressurizing compressor including a drive motor that rotates two crankshafts.
As shown in FIGS. 16 to 18, the drive device 10 as a compressor includes a rectangular box-shaped crankcase 70, a cylinder block 72 having two cylinders 22 a and 22 b and provided on the crankcase 70, and a cylinder A cylinder head 74 that covers the upper openings of 22a and 22b, and a first crankshaft 12a and a second crankshaft 12b that are rotatably supported in the crankcase 70, respectively. The crankcase 70 is installed on a plate-like base 76.

  In the present embodiment, the two cylinders 22a and 22b are formed in parallel with each other and have the same inner diameter. The central axes of the cylinders 22 a and 22 b extend perpendicular to the base 76. The cylinder head 74 is provided with a first reed valve 78a for controlling intake air to the cylinder 22a and exhaust from the cylinder 22a, and a second reed valve 78b for controlling intake air to the cylinder 22b and exhaust from the cylinder 22b. It has been.

  The drive device 10 has a first drive unit 20a having a first piston 24a and a first crankshaft 12a provided in the cylinder 22a, and a second piston 24b and a second crankshaft 12b provided in the cylinder 22b. The second drive unit 20b, the first crankshaft 12a and the second crankshaft 12b are connected, a connection synchronization mechanism 50 that rotates the first crankshaft and the second crankshaft in synchronization, and the first crankshaft 12a A first drive motor 80a that drives (rotates) and a second drive motor 80b that drives (rotates) the second crankshaft 12b in a direction opposite to the first crankshaft 12a are provided. The first drive motor 80a and the second drive motor 80b have, for example, the same size and the same output, and are installed on the base 76 and arranged on both sides of the crankcase 70, respectively.

  As shown in FIG. 18, the first drive unit 20a and the second drive unit 20b have the same configuration. The first drive unit 20a and the second drive unit 20b are arranged so that the first direction X1 that is the moving direction of the first piston 24a and the second direction X2 that is the moving direction of the second piston 24b are parallel to each other. Has been. The first drive unit 20a and the second drive unit 20b are respectively disposed on both sides of the center reference plane CRP, and further, the first drive unit 20a and the second drive unit 20b are left and right, front and rear with respect to the center reference plane CRP. They are arranged symmetrically (mirror arrangement) and configured. The first drive unit 20a is provided on the first installation plane MP1 positioned on one side of the center reference plane CRP and orthogonal to the center reference plane CRP, and the second drive unit 20b is positioned on the opposite side of the center reference plane CRP and centered. It is provided on a second installation plane MP2 that is orthogonal to the reference plane CRP, that is, a second installation plane MP2 that is symmetrical to the first installation plane MP1.

  According to the present embodiment, the first drive unit 20a includes a first crankshaft 12a extending orthogonally to the first installation plane MP1, and the first piston 24a and the first crankshaft 12a within the first installation plane MP1. A first XY separation crank mechanism 30a is provided between the first piston 24a and the reciprocating motion of the first piston 24a and the rotational motion of the first crankshaft 12a. The first direction, which is the reciprocating direction of the first piston 24a, is a first direction X1 parallel to the center reference plane CRP. The first crankshaft 12a is disposed substantially parallel to the center reference plane CRP.

  The second drive unit 20b is provided between the second piston 24b and the second crankshaft 12b in the second installation plane MP2, and between the second crankshaft 12b extending perpendicularly to the second installation plane MP2, A second XY separation crank mechanism 30b that mutually converts the reciprocating motion of the piston 24b and the rotational motion of the second crankshaft 12b. A second direction that is the reciprocating direction of the second piston 24a is a second direction X2 that is parallel to the first direction X1 described above and parallel to the center reference plane CRP.

  The first XY separation crank mechanism 30a and the second XY separation crank mechanism 30b have the same configuration and are arranged symmetrically with respect to the center reference plane CRP in the left-right direction. The second XY separation crank mechanism 30b will be described in detail as a representative. As shown in FIGS. 18 and 19, the second XY separation crank mechanism 30b reciprocates along the second direction X2 on the second installation plane MP2 including the central axis (movement axis, X axis) of the second piston 24b. A second support member (combinator) 32b provided freely and a second support member 32b reciprocally movable along a fourth direction Y2 (Y-axis direction) orthogonal to the second direction X2 on the second installation plane MP2. And a second connecting rod 36b as a connecting member for connecting the second piston 24b and the second support member 32b. The movement center axis of the second support member 32b (second direction X2), the movement center axis of the second crank connecting member 34b (fourth direction Y2), and the center movement axis of the second connecting rod 36b (second direction X2) are as follows. , Located on the second installation plane MP2.

  In the present embodiment, the second support member 32b is formed in a rectangular frame shape, for example. That is, the second support member 32b includes a first support portion 35a extending in the second direction X2, and a second support portion 35b and a third support portion 35c extending in the fourth direction Y2 from both axial ends of the first support portion 35a. Is integrated. In the present embodiment, the second support member 32b connects the extended end of the second support portion 35b and the extended end of the third support portion 35c, and faces the first support portion 35a with a gap therebetween. A support portion 35d is provided. The mutually opposing inner surfaces of the second support part 35b and the third support part 35c are formed flat and parallel to each other and extend along the fourth direction Y2. The second support member 32b is die-cast, for example, with aluminum.

  The second linear slider 41a is fixed to the first support portion 35a. A second guide rail 45a is installed on the inner surface of the crankcase 70, and extends in the second direction X2 within the second installation plane MP2. The second linear slider 41a is supported and guided by the second guide rail 45a so as to reciprocate. Thereby, only the 1st support part 35a is supported on the 2nd guide rail 45a so that reciprocation is possible along the 2nd direction X2 among the 2nd support members 32b. The second linear slider 41a may incorporate a ball bearing that is in rolling contact with the second guide rail 45a.

  The second crank connecting member 34b is configured as a rectangular block-shaped member. The upper and lower side surfaces of the crank connecting member 34b constitute a first sliding surface 60a and a second sliding surface 60b, respectively. The first sliding surface 60a and the second sliding surface 60b are formed to be flat and parallel, and extend along the fourth direction Y2.

  A circular through hole 46 is formed through substantially the center of the second crank connecting member 34b. The through hole 46 extends in the Z-axis direction orthogonal to the second direction X2 and the fourth direction Y2, that is, in a direction parallel to the second crankshaft 12b. The crank pin 16b of the second crankshaft 12b is rotatably inserted into the through hole 46. A plain bearing is formed on the sliding surface, that is, the inner surface of the through hole 46 by lining processing (plating) such as electroforming or electrodeposition. A wire cut may be used after plating.

  The second crank connecting member 34b is disposed in the frame-shaped second support member 32b, the first sliding surface 60a slidably contacts the inner surface of the second support portion 35b, and the second sliding surface 60b It is slidably in contact with the inner surface of the third support portion 35c. Thereby, the second crank connecting member 34b is supported and guided between the second and third support portions 35b and 35c of the second support member 32b so as to reciprocate along the fourth direction Y2. Further, the crank pin 16b of the second crankshaft 12b is rotatably inserted into the through hole 46 of the second crank connecting member 34b. Thus, the second crank connecting member 34b is engaged with the second crankshaft 12, and connects the second crankshaft 12b and the second support member 32b.

  Note that guide rails extending in the fourth direction Y2 are installed on the inner surfaces of the second support portion 35b and the third support portion 35c of the second support member 32b, respectively, and the first sliding surface 60a of the second crank connection member 34b. In addition, guide grooves that engage with the guide rails may be provided in the second sliding surface 60b.

  The second crank connecting member 34b is divided into two members (a first half portion 64a including a first sliding surface 60a, and a first half surface 64a, which are divided along a dividing surface 62 that passes through the central axis of the through hole 46 and is orthogonal to the second direction X2. The second half portion 64b including the second sliding surface 60b) is engaged, and the two members are engaged in a state where the divided surfaces 62 face each other, thereby forming a crank connecting member 34b having a rectangular block shape. Yes. The dividing surface 62 is a surface that passes through the central axis of the through hole 46 and extends in the fourth direction Y2. Further, the dividing surface 62 is formed in a corrugated surface having a wave shape, an S shape, or a cyclone shape. The unevenness of the dividing surface 62 is alternately arranged in the Z-axis direction (the axial direction of the through hole 46), and the respective recesses and protrusions extend in the fourth direction Y2. In the present embodiment, each divided surface 62 has arcuate concave surfaces and arcuate convex surfaces that are alternately arranged. In the engaged state, the gap between the dividing surface 61 of the first half portion 64a and the dividing surface 61 of the second half portion 64b is formed to be about 100 μm. The first and second half portions 64a and 64b are preferably formed of a material that easily contains lubricating oil, such as copper, brass, or fine ceramic. Further, the first and second half portions 64a and 64b can be made of engineering plastics such as ABS, and can be made by performing vapor deposition plating or the like on the surface.

  In addition, each division surface 62 of the 1st half part 64a and the 2nd half part 64b is good also as an uneven surface which has a 2 or more convex part and / or a 2 or more recessed part. In addition, the concave / convex surface only needs to have concave portions and convex portions arranged in the Z-axis direction, and the shapes of the concave portions and the convex portions themselves are not limited to curved surfaces but can be variously changed to other shapes.

  One end of the second connecting rod 36b of the second XY separation crank mechanism 30b is connected to the second piston 24b via a support pin, and the other end is connected to the second support portion 35b of the second support member 32b. The second connecting rod 36b extends in parallel with the second direction X2 and coaxially with the second piston 24b. The second connecting rod 36b reciprocates integrally with the second support member 32b along the second direction X2, and reciprocates the second piston 24b along the second direction X2. The connecting member is not limited to a single connecting rod, and a plurality of connecting rods or a plate-like connecting arm extending in the fourth direction Y2 may be used.

  As shown in FIGS. 18 and 19, the first XY separation crank mechanism 30a is configured similarly to the second XY separation crank mechanism 30b, and reciprocates along the first direction X1 by the first linear slider 40a and the first guide rail 44a. A rectangular frame-shaped first support member 32a provided movably, and a block-shaped first crank connecting member 34a supported and guided in the first support member 32a so as to reciprocate along the third direction Y1. And a first connecting rod 36a connecting the first support member 32a and the first piston 24a. A crank pin of the first crankshaft 12a is rotatably inserted through the through hole of the first crank connecting member 34a.

The first XY separation crank mechanism 30 a and the second XY separation crank mechanism 30 b configured as described above are provided in the crankcase 70. The first XY separation crank mechanism 30a is arranged and configured symmetrically with the second XY separation crank mechanism 30b with respect to the center reference plane CRP, and operates symmetrically with the second XY separation crank mechanism 30b.
Both ends of the first crankshaft 12a in the axial direction pass through the side walls of the crankcase 70, and are rotatably supported on the crankcase 70 by bearings. The second crankshaft 12b extends in parallel with the first crankshaft 12a, and both axial ends thereof penetrate the side walls of the crankcase 70, respectively, and are rotatably supported by the crankcase 70 by bearings.

  As shown in FIGS. 16 to 18, the connection synchronization mechanism 50 of the driving device 10 is provided with a first gear 52 a coaxially attached to one end of the first crankshaft 12 a and one end of the second crankshaft 12 b. And a second gear 52b attached coaxially. The first gear 52a and the second gear 52b are formed to have the same diameter and the same number of teeth, and mesh with each other. The first crankshaft 12a and the second crankshaft 12b are connected to each other via a first gear 52a and a second gear 52b. In order to avoid interference between the first gear 52 a and the second gear 52 b and the base 76, a slot 81 is formed in the base 76, and lower end portions of the first gear 52 a and the second gear 52 b are located in the slot 81. . When the first gear 52a rotates, the second gear 52b rotates in the opposite direction to the first gear 52a in synchronization with the rotation of the first gear 52a. Thereby, the 1st crankshaft 12a and the 2nd crankshaft 12b rotate in the mutually opposite direction synchronously.

A first driven pulley 82a is coaxially attached to the other end of the first crankshaft 12a. A second driven pulley 82a is coaxially attached to the other end of the second crankshaft 12b. The first driven pulley 82a and the second driven pulley 82b are formed to have the same diameter. A first drive pulley 84a is coaxially attached to the drive shaft 81a of the first drive motor 80a, and a first drive belt 86a is stretched between the first drive pulley 84a and the first driven pulley 82a. A second drive pulley 84b is coaxially attached to the drive shaft 81b of the second drive motor 80b, and a second drive belt 86b is bridged between the second drive pulley 84b and the second driven pulley 82b. The first drive pulley 84a and the second drive pulley 84b are formed to have the same diameter. Each pulley and drive belt described above may be a toothed pulley and a toothed belt, respectively.
The transmission mechanism that transmits the rotational output of the drive motor to the crankshaft is not limited to the combination of the pulley and the belt, and may be configured by a combination of a sprocket and a chain.

  In the drive device 10 configured as a compressor as described above, when the first drive motor 80a and the second drive motor 80b are operated, the first drive pulley, the first drive belt, and the first driven pulley are used as the first drive motor 80a and the second drive motor 80b. The rotational force of the drive motor 80a is input to the first crankshaft 12a, and at the same time, the rotational force of the second drive motor 80b is passed through the second drive pulley, the second drive belt, and the second driven pulley. Is input. As a result, rotational forces in opposite directions are input to the first crankshaft 12a and the second crankshaft 12b, and the first crankshaft 12a and the second crankshaft 12b rotate in directions opposite to each other. At this time, the first and second crankshafts 12a and 12b rotate in synchronization with each other by the connection synchronization mechanism 50. The crankpin of each crankshaft rotates eccentrically around the crankshaft.

  The eccentric rotational movement of the crank pin 16a of the first crankshaft 12a is caused by the reciprocating movement in the third direction Y1 and the first direction X1 by the first crank connecting member 34a and the first support member 32a of the first XY separation crank mechanism 30a. The reciprocating motion is separated into the reciprocating motion, and the reciprocating motion in the first direction X1 of the first support member 32a is transmitted to the first piston 24a via the first connecting rod 36a. Thus, the first piston 24a reciprocates along the first direction X1 in the first cylinder 22a, compresses the fluid in the first cylinder 22a, and then outputs the pressurized fluid through the first reed valve 78a.

  Similarly, the eccentric rotational motion of the crank pin 16b of the second crankshaft 12b is the same as the reciprocating motion in the fourth direction Y2 by the second crank connecting member 34b and the second support member 32b of the second XY separation crank mechanism 30b. The reciprocating motion in the direction X2 is separated, and the reciprocating motion in the second direction X2 of the second support member 32b is transmitted to the second piston 24b via the second connecting rod 36b. Thus, the second piston 24b reciprocates along the second direction X2 in the second cylinder 22b, compresses the fluid in the second cylinder 22b, and then outputs the pressurized fluid through the second reed valve 78b.

  Since the first drive unit 20a and the second drive unit 20b are arranged and configured symmetrically with respect to the center reference plane CRP, the operation is also symmetric. When the first piston 24a moves to the top dead center, the second piston 24b also moves to the top dead center in synchronization with this. When the first piston 24a moves from the top dead center toward the bottom dead center, at the same time, the second piston 24b moves from the top dead center toward the bottom dead center. The first XY separation crank mechanism 30a and the second XY separation crank mechanism 30b also operate in synchronization with each other while maintaining a symmetric state with respect to the center reference plane CRP.

  According to the drive device 10 configured as described above, in the first drive unit 20a and the second drive unit 20b, the first and second XY separation crank mechanisms 30a and 30b cause the rotational motion and the first motion of the first crankshaft 12a. The rotational movement of the two crankshafts 12b is divided into linear reciprocating movements in the first direction and the second direction, and linear reciprocating movements in the third direction and the fourth direction orthogonal to the first direction and the second direction, respectively. They can be separated and converted, and a complete parallel movement of the first piston 24a and the second piston 24b can be realized. Therefore, it is possible to eliminate the contact of the piston with the cylinder, to improve the sealing performance, to reduce the friction loss, and to achieve high efficiency with no side thrust loss. In addition, the first drive unit and the second drive unit are arranged symmetrically with respect to the central reference plane and symmetrically in the front-rear direction (mirror arrangement). A structure can be constructed.

  In addition, the side thrust of the piston can be substantially eliminated by the XY separation crank mechanism. As a result, the cylinder and piston can be formed of ceramic, glass, etc. Can be built. Furthermore, since the drive device is not vibrated by side thrust, the cylinder can be formed of carbon fiber or a plastic material such as PBT. Furthermore, because of the side thrust stress, a high aspect ratio of the piston can be realized, and accordingly, a short and short stroke can be achieved and a small low profile compressor or pump can be realized.

  Furthermore, according to the eleventh embodiment, the support member in the XY separation crank mechanism has a U-shaped frame shape, and the crank connecting member is slidably arranged in the XYZ directions in the frame body, thereby providing a linear guide. And the number of constituent members of the XY separation crank mechanism can be reduced. Further, at the time of assembly, the crank connecting member is divided and mounted on the crankshaft, and after mounting, the crank connecting member is mounted between the second support portion and the third support portion of the support member. Thereby, a crank connection member can be assembled | attached with respect to the 1st and 2nd crankshafts 12a and 12b which have a crankpin. As a result, the number of man-hours for assembling the crank mechanism can be reduced, and even in the case of multiple cylinders, the assembly can be facilitated and the assemblability can be improved. Furthermore, the support member and the crank connecting member can have a function of automatically adjusting the sliding at the optimum position.

  The crank connecting member is divided into two on the left and right sides of the central axis of the through hole 46, and the dividing surface 62 is formed in an uneven shape so that there is an opening in the XY direction between the divided first half portion 64a and second half portion 64b. However, inconvenience due to mutual interference can be prevented. When the uneven shape is a wave shape, an S shape, or a cycloid shape, mutual interference between the two members can be removed even in the ZY plane perpendicular to the Z-axis direction. By forming the clearance between the two members with a small gap of about 100 μm, for example, it is possible to insulate a three-dimensional force between the XY plane and the ZY plane. At the same time, automatic alignment in the Z-axis direction between the two members can be performed.

  As described above, according to the present embodiment, a mirror type XY separation crank mechanism that reversely couples two crankshafts with a gear or a belt to reduce vibrations and an automatic XYZ force separation mechanism are combined. In addition, a compressor or a pump that reduces friction loss and vibration and has high operating efficiency can be obtained. Since the cylinder and the piston can be arranged next to each other, collective piping is easy. Since the conventional crosshead is unnecessary and there is no vibration, the entire apparatus can be reduced in weight. In addition, since the two crankshafts are fully synchronous, simultaneous forward rotation, and reverse rotation, the crankshaft can be driven using two independent drive motors, and each drive motor can be a small and inexpensive motor. Can be used.

  The number of drive motors is not limited to two, and a single drive motor may be used. In this case, a rotational force is input to one of the crankshafts by the drive motor, and the rotational force is transmitted to the other crankshaft by the connection synchronization mechanism. The shape of the piston is not limited to a circle, and may be a non-circular shape, for example, an oval shape, a rectangular shape with rounded corners, other polygonal shapes, an elliptical shape with a narrowed central portion, or the like.

(Twelfth embodiment)
20 is a perspective view showing the front side of the drive device according to the twelfth embodiment, FIG. 21 is a perspective view showing the back side of the drive device, and FIG. 22 is a front view showing the drive device with a part broken away. FIG. 23 is an exploded perspective view showing the XY separation crank mechanism of the drive device. According to the present embodiment, the drive device constitutes a two-axis output engine device.

  As shown in FIGS. 20 to 22, the drive device 10 is configured as an engine device that operates in two cycles, for example. The driving device 10 includes a rectangular box-shaped crankcase 70, an upper cylinder block (first cylinder block) 72a provided on the crankcase 70 having a first cylinder 22a and a second cylinder 22b, and first and first cylinders. A head cover (cam case) 88 that covers the upper openings of the two cylinders 22a and 22b, a lower cylinder block (second cylinder block) 72b that has a third cylinder 23a and a fourth cylinder 23b and that is provided under the crank case 70; A valve case 90 covering the lower openings of the third and fourth cylinders 23a and 23b, an air collector 92 provided on the lower surface of the valve case 90, a first crankshaft 12a rotatably supported in the crankcase 70, and A second crankshaft 12b. In the present embodiment, the first crankshaft 12a and the second crankshaft 12b are arranged in parallel to each other.

  In the present embodiment, the upper two first and second cylinders 22a and 22b are formed in parallel with each other and have the same inner diameter. The lower two third and fourth cylinders 23a and 23b are formed in parallel to each other and have the same inner diameter. The inner diameters of the third and fourth cylinders 23a and 23b are formed larger than the inner diameters of the first and second cylinders 22a and 22b. The upper first cylinder 22a and the lower third cylinder 23a are provided coaxially with each other and have a common central axis. The upper second cylinder 22b and the lower fourth cylinder 23b are provided coaxially with each other and have a common central axis.

  The head cover 88 includes a combustion chamber 94a communicating with the upper opening of the first cylinder 22a, an air supply port and an exhaust port opening to the combustion chamber 94a, and a combustion chamber communicating with the upper opening of the second cylinder 22b. 94b, an air supply port and an exhaust port that open to the combustion chamber 94b are formed. The head cover 88 includes a first air supply side valve mechanism 96a for opening and closing an air supply port on the first cylinder 22a side, a first exhaust side valve mechanism 98a for opening and closing an exhaust port on the first cylinder 22a side, and a second cylinder 22b. A second air supply side valve mechanism 96b for opening and closing the side air supply port and a second exhaust side valve mechanism 98b for opening and closing the exhaust port on the second cylinder 22b side are provided.

These valve mechanisms 96a, 96b, 98a, 98b have the same configuration. That is, each valve mechanism is, for example, a mushroom valve 100, a valve slider 102 connected to the stem of the mushroom valve 100, and a valve slider 102 fixed to the head cover 88 and sliding the valve slider 102 in the opening / closing direction of the mushroom valve 100. A linear guide 104 that freely guides, a valve spring 106 that is provided between the valve slider 102 and the head cover 88 and biases the mushroom valve 100 toward the closed position, and a cam follower 107 that is rotatably attached to the valve slider 102. The rocker arm 108 is swingably attached to the head cover 88 and has one end abutting against the cam follower 107 and a plurality of cams contacting the other end of the rocker arm 108, and is rotatably supported by the head cover 88. And a common camshaft 110.
Further, ignition plugs 95a and 95b are attached to the head cover 88 and face the combustion chambers 94a and 94b, respectively.

  On the other hand, the lower valve case 90 is provided with a first reed valve 78a for controlling intake to the third cylinder 23a and a second reed valve 78b for controlling intake to the fourth cylinder 23b. Further, an exhaust reed valve 79 is provided in the valve case 90. The exhaust reed valve 79 controls the exhaust of compressed gas from the third cylinder 23a and the fourth cylinder 23b. The drive device 10 has an exhaust passage (exhaust pipe) 112 extending from the exhaust reed valve 79 to the two intake ports of the head cover 88. In the present embodiment, the exhaust passage 112 is defined by a flow hole formed continuously in the lower cylinder block 72 b, the crankcase 70, the upper cylinder block 72 a, and the head cover 88. As will be described later, the compressed gas exhausted from the third cylinder 23 a and the fourth cylinder 23 b passes through the exhaust reed valve 79, the exhaust flow path 112, and the intake port of the head cover 88, and then the first cylinder 22 a and the second cylinder 22 b. It is supplied to the combustion chambers 94a and 94b.

  As shown in FIGS. 20 to 22, the driving apparatus 10 has a first drive unit 20a for driving the first crankshaft 12a and a second crankshaft 12b having the same configuration as the first drive unit 20a. And a connection synchronization mechanism 50 that connects the first crankshaft 12a and the second crankshaft 12b and rotates the first crankshaft and the second crankshaft in synchronization with each other. The first drive unit 20a and the second drive unit 20b are respectively disposed on both sides of the center reference plane CRP, and further, the first drive unit 20a and the second drive unit 20b are left and right, front and rear with respect to the center reference plane CRP. They are arranged symmetrically (mirror arrangement) and configured. The first drive unit 20a is provided on the first installation plane MP1 positioned on one side of the center reference plane CRP and orthogonal to the center reference plane CRP, and the second drive unit 20b is positioned on the opposite side of the center reference plane CRP and centered. It is provided on a second installation plane MP2 that is orthogonal to the reference plane CRP, that is, a second installation plane MP2 that is symmetrical to the first installation plane MP1. The first crankshaft 12a extends perpendicular to the first installation plane MP1. The second crankshaft 12b extends perpendicular to the second installation plane MP2.

  The first drive unit 20a includes a first piston 24a provided in a reciprocating manner in the first cylinder 22a, a first crankshaft 12a described above, and a third piston provided in a reciprocating manner in the third cylinder 23a. The piston 25a is provided between the first piston 24a and the first crankshaft and between the third piston 25a and the first crankshaft. The reciprocating motion of the first piston 24a and the third piston 25a and the first crankshaft And a first XY separation crank mechanism 30a that mutually converts the rotational motion of 12a. A first direction which is a reciprocating direction of the first piston 24a and the third piston 25a is a first direction X1 parallel to the center reference plane CRP. In the present embodiment, the lower third piston 25a is formed to have a larger diameter than the upper first piston 24a, and further has a larger aspect ratio.

  The second drive unit 20b includes a second piston 24b that is reciprocally provided in the second cylinder 22b, a second crankshaft 12b, and a fourth cylinder 23b that is reciprocally provided in the fourth cylinder 23b. The piston 25b is provided between the second piston 24b and the second crankshaft 12b and between the fourth piston 25b and the second crankshaft. The reciprocating motion of the second piston 24b and the fourth piston 25b and the second crank And a second XY separation crank mechanism 30b that mutually converts the rotational movement of the shaft 12b. A second direction that is the reciprocating direction of the second piston 24b and the fourth piston 25b is a second direction X2 that is parallel to the first direction X1 and parallel to the center reference plane CRP. In the present embodiment, the lower fourth piston 25b is formed to have a larger diameter than the upper second piston 24b, and has a larger aspect ratio (diameter / height).

  The first XY separation crank mechanism 30a and the second XY separation crank mechanism 30b have the same configuration and are arranged symmetrically with respect to the center reference plane CRP in the left-right direction. The second XY separation crank mechanism 30b will be described in detail as a representative. As shown in FIGS. 22 and 23, the second XY separation crank mechanism 30b has a second installation plane MP2 including the central axis (movement axis, X axis) of the second piston 24b and the central axis of the fourth piston 25b. In the second support member (combinator) 32b provided so as to be able to reciprocate along the two directions X2, and in the second installation plane MP2, it reciprocates along the fourth direction Y2 (Y-axis direction) orthogonal to the second direction X2. A second crank connecting member (crank connecting plate) 34b movably attached to the second support member 32b; a second connecting rod 36b as a connecting member for connecting the second piston 24b and the second support member 32b; And a fourth connecting rod 37b as a connecting member for connecting the fourth piston 25b and the second support member 32b. The movement center axis of the second support member 32b (second direction X2), the movement center axis of the second crank connecting member 34b (fourth direction Y2), and the center movement axis of the second and fourth connecting rods 36b and 37b (first The two directions X2) are located on the second installation plane MP2.

  In the present embodiment, the second support member 32b is formed in a rectangular frame shape, for example. That is, the second support member 32b includes a first support portion 35a extending in the second direction X2, and a second support portion 35b and a third support portion 35c extending in the fourth direction Y2 from both axial ends of the first support portion 35a. Is integrated. In the present embodiment, the second support member 32b connects the extended end of the second support portion 35b and the extended end of the third support portion 35c, and faces the first support portion 35a with a gap therebetween. A support portion 35d is provided. The mutually opposing inner surfaces of the second support part 35b and the third support part 35c are formed flat and parallel to each other and extend along the fourth direction Y2. The second support member 32b is die-cast, for example, with aluminum.

  The second linear slider 41a is fixed to the first support portion 35a. A second guide rail 45a is installed on the inner surface of the crankcase 70, and extends in the second direction X2 within the second installation plane MP2. The second linear slider 41a is supported and guided by the second guide rail 45a so as to reciprocate. Thereby, only the 1st support part 35a is supported on the 2nd guide rail 45a so that reciprocation is possible along the 2nd direction X2 among the 2nd support members 32b. The second linear slider 41a may incorporate a ball bearing that is in rolling contact with the second guide rail 45a.

  The second crank connecting member 34b is configured as a rectangular block-shaped member. The upper and lower side surfaces of the crank connecting member 34b constitute a first sliding surface 60a and a second sliding surface 60b, respectively. The first sliding surface 60a and the second sliding surface 60b are each formed flat and parallel to each other, and each extend along the fourth direction Y2.

  A circular through hole 46 is formed through substantially the center of the second crank connecting member 34b. The through hole 46 extends in the Z-axis direction orthogonal to the second direction X2 and the fourth direction Y2, that is, in a direction parallel to the second crankshaft 12b. The crank pin 16b of the second crankshaft 12b is rotatably inserted into the through hole 46. A plain bearing is formed on the sliding surface, that is, the inner surface of the through hole 46 by lining processing (plating) such as electroforming or electrodeposition. A wire cut may be used after plating.

  The second crank connecting member 34b is disposed in the frame-shaped second support member 32b, the first sliding surface 60a slidably contacts the inner surface of the second support portion 35b, and the second sliding surface 60b It is slidably in contact with the inner surface of the third support portion 35c. Thereby, the second crank connecting member 34b is supported and guided between the second and third support portions 35b and 35c of the second support member 32b so as to reciprocate along the fourth direction Y2. Further, the crank pin 16b of the second crankshaft 12b is rotatably inserted into the through hole 46 of the second crank connecting member 34b. Thus, the second crank connecting member 34b is engaged with the second crankshaft 12, and connects the second crankshaft 12b and the second support member 32b.

  Note that guide rails extending in the fourth direction Y2 are installed on the inner surfaces of the second support portion 35b and the third support portion 35c of the second support member 32b, respectively, and the first sliding surface 60a of the second crank connection member 34b. In addition, guide grooves that engage with the guide rails may be provided in the second sliding surface 60b.

  The second crank connecting member 34b is divided into two members (a first half portion 64a including a first sliding surface 60a, and a first half surface 64a, which are divided along a dividing surface 62 that passes through the central axis of the through hole 46 and is orthogonal to the second direction X2. The second half portion 64b including the second sliding surface 60b) is engaged, and the two members are engaged in a state where the divided surfaces 62 face each other, thereby forming a crank connecting member 34b having a rectangular block shape. Yes. The dividing surface 62 is a surface that passes through the central axis of the through hole 46 and extends in the fourth direction Y2. Further, the dividing surface 62 is formed in a corrugated surface having a wave shape, an S shape, or a cyclone shape. The unevenness of the dividing surface 62 is alternately arranged in the Z-axis direction (the axial direction of the through hole 46), and the respective recesses and protrusions extend in the fourth direction Y2. In the present embodiment, each divided surface 62 has arcuate concave surfaces and arcuate convex surfaces that are alternately arranged. In the engaged state, the gap between the dividing surface 61 of the first half portion 64a and the dividing surface 61 of the second half portion 64b is formed to be about 100 μm. The first and second half portions 64a and 64b are preferably formed of a material that easily contains lubricating oil, such as copper, brass, or fine ceramic. Further, the first and second half portions 64a and 64b can be made of engineering plastics such as ABS, and can be made by performing vapor deposition plating or the like on the surface.

  In addition, each division surface 62 of the 1st half part 64a and the 2nd half part 64b is good also as an uneven surface which has a 2 or more convex part and / or a 2 or more recessed part. In addition, the concave / convex surface only needs to have concave portions and convex portions arranged in the Z-axis direction, and the shapes of the concave portions and the convex portions themselves are not limited to curved surfaces but can be variously changed to other shapes.

  One end of the second connecting rod 36b of the second XY separation crank mechanism 30b is connected to the second piston 24b via a support pin, and the other end is connected to the second support portion 35b of the second support member 32b. The second connecting rod 36b extends in parallel with the second direction X2 and coaxially with the second piston 24b. The second connecting rod 36b reciprocates integrally with the second support member 32b along the second direction X2, and reciprocates the second piston 24b along the second direction X2.

  One end of the second connecting rod 36b of the second XY separation crank mechanism 30b is connected to the second piston 24b via a support pin, and the other end is connected to the second support portion 35b of the second support member 32b. The second connecting rod 36b extends in parallel with the second direction X2 and coaxially with the second piston 24b. The second connecting rod 36b reciprocates integrally with the second support member 32b along the second direction X2, and reciprocates the second piston 24b along the second direction X2.

One end of the fourth connecting rod 37b of the second XY separation crank mechanism 30b is connected to the fourth piston 25b via a support pin, and the other end is connected to the third support portion 35c of the second support member 32b. The fourth connecting rod 37b extends in parallel with the second direction X2 and coaxially with the fourth piston 25b. The fourth connecting rod 37b reciprocates integrally with the second support member 32b along the second direction X2, and reciprocates the fourth piston 25b along the second direction X2.
The connecting member is not limited to a single connecting rod, and a plurality of connecting rods or a plate-like connecting arm extending in the fourth direction Y2 may be used.

  As shown in FIGS. 22 and 23, the first XY separation crank mechanism 30a is configured similarly to the second XY separation crank mechanism 30b, and reciprocates along the first direction X1 by the first linear slider 40a and the first guide rail 44a. A rectangular frame-shaped first support member 32a provided movably, and a block-shaped first crank connecting member 34a supported and guided in the first support member 32a so as to reciprocate along the third direction Y1. The first connecting rod 36a connecting the first support member 32a and the first piston 24a and the third connecting rod 37a connecting the first support member 32a and the third piston 25a are provided. A crank pin of the first crankshaft 12a is rotatably inserted through the through hole of the first crank connecting member 34a.

  The first crank connecting member 34a is divided into two members (a first half portion including a first sliding surface, and a second sliding member) divided along a dividing surface 62 that passes through the central axis of the through hole and is orthogonal to the first direction X1. A rectangular block-shaped crank connecting member 34a is formed by engaging these two members with the divided surfaces 62 facing each other. The dividing surface 62 is a surface that passes through the central axis of the through hole and extends in the second direction Y1. Further, the dividing surface 62 is formed in a corrugated surface having a wave shape, an S shape, or a cyclone shape. The unevenness of the dividing surface 62 is alternately arranged in the Z-axis direction (the axial direction of the through hole), and the respective recesses and protrusions extend in the second direction Y1.

The first XY separation crank mechanism 30 a and the second XY separation crank mechanism 30 b configured as described above are provided in the crankcase 70. The first XY separation crank mechanism 30a is arranged and configured symmetrically with the second XY separation crank mechanism 30b with respect to the center reference plane CRP, and operates symmetrically with the second XY separation crank mechanism 30b.
Both ends of the first crankshaft 12a in the axial direction pass through the side walls of the crankcase 70, and are rotatably supported on the crankcase 70 by bearings. The second crankshaft 12b extends in parallel with the first crankshaft 12a, and both axial ends thereof penetrate the side walls of the crankcase 70, respectively, and are rotatably supported by the crankcase 70 by bearings.

  As shown in FIGS. 20 to 22, the connection synchronization mechanism 50 of the driving device 10 includes a first gear 52 a coaxially attached to one end portion of the first crankshaft 12 a and one end portion of the second crankshaft 12 b. And a second gear 52b attached coaxially. The first gear 52a and the second gear 52b are formed to have the same diameter and the same number of teeth, and mesh with each other. The first crankshaft 12a and the second crankshaft 12b are connected to each other via a first gear 52a and a second gear 52b. When the first gear 52a rotates, the second gear 52b rotates in the opposite direction to the first gear 52a in synchronization with the rotation of the first gear 52a. Thereby, the 1st crankshaft 12a and the 2nd crankshaft 12b rotate in the mutually opposite direction synchronously.

  A first timing pulley 114a is coaxially attached to the other end of the first crankshaft 12a. A second timing pulley 114b is coaxially attached to the other end of the second crankshaft 12b. A third timing pulley 114 c is attached to one end of the camshaft 110 attached to the head cover 88. Further, a rotatable idler pulley 116 is provided in the vicinity of the second timing pulley 114b. The idler pulley 116 is supported by the crankcase 70, for example.

A cam timing belt 114 is stretched around the first, second, and third timing pulleys 114a, 114b, and 114c and the idler pulley 116. Each timing pulley and idler pulley 116 is a toothed pulley. The timing belt 114 is a toothed belt having teeth on both sides. The first, second, and third timing pulleys 114a, 114b, and 114c, the idler pulley 116, and the cam timing belt 114 rotate the camshaft 110 in synchronization with the rotation of the first and second crankshafts 12a and 12b. The intake side and exhaust side valves can be opened and closed at a predetermined timing.
The mechanism for rotating the crankshaft 110 is not limited to a combination of a toothed pulley and a toothed belt, and a combination of a sprocket and a chain may be used.

  In the drive device 10 configured as an engine device as described above, at the time of starting, the first crank shaft 12a and the second crank shaft 12b are rotated by a motor (not shown) or the like, and the first to fourth pistons 24a, 24b, 25a are rotated. , 25b is moved up and down. For example, as shown in FIG. 22, while the first and second pistons 24a, 24b move from the bottom dead center to the top dead center, the first intake valve and the second intake valve are opened, and air and fuel are discharged from the intake port. Is supplied to the first and second cylinders 22a, 22b and the combustion chambers 94a, 94b, and then the first intake valve and the second intake valve are closed, and the fuel-air mixture is compressed. Subsequently, the air-fuel mixture in the combustion chambers 94a and 94b is ignited by the spark plugs 95a and 95b, and the first and second pistons 24a and 24b are lowered from the top dead center toward the bottom dead center by burning and exploding. . During this time, the first exhaust valve and the second exhaust valve are opened, and the combustion gas is exhausted from the exhaust port in the latter half of the lowering of the piston. After the start, the first and second pistons 24a and 24b are driven to reciprocate in the first direction X1 and the second direction X2 by repeating air supply and combustion. The reciprocating motion of the first and second pistons 24a and 24b is converted into rotational motion by the first XY separation crank mechanism 30a and the second XY separation crank mechanism 30b, and rotational force is input to the first and second crankshafts 12a and 12b, respectively. Is done. As a result, the first crankshaft 12a and the second crankshaft 12b rotate in directions opposite to each other. At this time, the first and second crankshafts 12a and 12b rotate in synchronization with each other by the connection synchronization mechanism 50.

  Further, the third and fourth pistons 25a and 25b are driven to reciprocate in the first direction X1 and the second direction X2 in synchronization with the reciprocating motion of the first and second pistons 24a and 24b. While the third and fourth pistons 25a, 25b move from the lowered position to the raised position, outside air is sucked into the second cylinder 23a and the fourth cylinder 23b from the first reed valve 78a and the second reed valve 78b. While the third and fourth pistons 25a and 25b move from the raised position to the lowered position, the air in the second cylinder 23a and the fourth cylinder 23b is compressed by the third and fourth pistons, and this compressed gas is exhausted. The air is exhausted from the reed valve 79 to the exhaust passage 112. Further, the compressed gas is sent to the intake port of the head cover 88 through the exhaust passage 112, and is supplied to the combustion chambers 94a and 94b through the first intake valve and the second intake valve. The third and fourth pistons 25a, 25b repeat reciprocating movements in the first direction X1 and the second direction X2, thereby repeating supply air and exhaust of compressed gas. Thus, the second and fourth cylinders 23a and 23b and the second and fourth pistons 25a and 25b can function as a pump or a turbocharger.

  Since the first drive unit 20a and the second drive unit 20b are arranged and configured symmetrically and anteroposteriorly with respect to the center reference plane CRP, the operations of these units are also symmetric. When the first piston 24a moves to the top dead center, the second piston 24b also moves to the top dead center in synchronization with this. When the first piston 24a moves from the top dead center toward the bottom dead center, at the same time, the second piston 24b moves from the top dead center toward the bottom dead center. Similarly, the second piston 25a and the fourth piston 25b move up and down in synchronization with each other.

  According to the drive device 10 configured as described above, in the first drive unit 20a and the second drive unit 20b, the first and second XY separation crank mechanisms 30a and 30b cause the rotational motion and the first motion of the first crankshaft 12a. The rotational motion of the two crankshafts 12b is changed into linear reciprocation in the first direction X1 and second direction X2 and linear in the third direction Y1 and fourth direction Y2 orthogonal to the first direction and the second direction, respectively. It can be separated and converted into reciprocating motion, and complete parallel motion of the first piston 24a and the second piston 24b and complete parallel motion of the third piston 25a and the fourth piston 25b can be realized. Therefore, it is possible to eliminate the contact of the piston with the cylinder, to improve the sealing performance, to reduce the friction loss, and to achieve high efficiency with no side thrust loss. In addition, the first drive unit and the second drive unit are arranged symmetrically with respect to the central reference plane and symmetrically in the front-rear direction (mirror arrangement). A structure can be constructed.

  The side thrust of the piston can be substantially eliminated by the XY separation crank mechanism. As a result, the cylinder and piston can be formed of ceramic, glass, etc., and a low-temperature, heat-retaining engine device with high thermal efficiency can be constructed. can do. Furthermore, since the drive device is not vibrated by side thrust, the cylinder can be formed of carbon fiber or a plastic material such as PBT. Furthermore, because of the side thrust, it is possible to realize a high aspect ratio of the piston, and accordingly, a short and short stroke can be achieved, thereby realizing a small low profile engine device.

  According to the present embodiment, the support member in the XY separation crank mechanism has a U-shaped frame shape, and the crank connection member is slidably arranged in the XYZ directions in the frame body, thereby omitting the linear guide, It is possible to reduce the number of constituent members of the XY separation crank mechanism. Further, at the time of assembly, the crank connecting member is divided and mounted on the crankshaft, and after mounting, the crank connecting member is mounted between the second support portion and the third support portion of the support member. Thereby, a crank connection member can be assembled | attached with respect to the 1st and 2nd crankshafts 12a and 12b which have a crankpin. As a result, the number of man-hours for assembling the crank mechanism can be reduced, and even in the case of multiple cylinders, the assembly can be facilitated and the assemblability can be improved. Furthermore, the support member and the crank connecting member can have a function of automatically adjusting the sliding at the optimum position.

  The crank connecting member is divided into two on the left and right sides of the central axis of the through hole 46, and the dividing surface 62 is formed in an uneven shape so that there is an opening in the XY direction between the divided first half portion 64a and second half portion 64b. However, inconvenience due to mutual interference can be prevented. When the uneven shape is a wave shape, an S shape, or a cycloid shape, mutual interference between the two members can be removed even in the ZY plane perpendicular to the Z-axis direction. By forming the clearance between the two members with a small gap of about 100 μm, for example, it is possible to insulate a three-dimensional force between the XY plane and the ZY plane. At the same time, automatic alignment in the Z-axis direction between the two members can be performed.

  Furthermore, according to the present embodiment, the third and fourth pistons that operate in synchronization with the first and second pistons that are combustion pistons are provided, and the supercharger (turbo pump) is provided by these third and fourth pistons. Is configured. Thereby, compressed (pressurized) gas can be supplied to the combustion chamber together with the fuel, and the combustion efficiency can be improved. Various engine devices such as a two-cycle turbo engine, a four-cycle turbo engine, and a diesel engine can be easily realized. In this embodiment, the shape of the piston is not limited to the oval shape, and other non-circular shapes such as a rectangular shape with rounded corners, other polygonal shapes, a constricted elliptical shape at the center, and the like. Also good.

(First modification)
In the twelfth embodiment described above, the engine device is not limited to two cycles, and may be a four-cycle engine device. FIG. 24 is a diagram schematically showing a supercharging mechanism according to a first modification suitable for a four-cycle engine device.
As shown in the figure, the supercharging mechanism has an exhaust pipe 130 that forms an exhaust passage 112. One end of the exhaust pipe 130 is connected to the exhaust port of the lower second (third) cylinders 23a, 23b, and the other end is connected to the intake port of the upper first (second) cylinders 22a, 22b. . The exhaust pipe 130 is provided with an intercooler 124 and an accumulation chamber 126, and a relief valve 128 is connected to the accumulation chamber 126. A carburetor 120 is connected to the intake ports of the lower second (third) cylinders 23a and 23b. In the case of a 4-cycle engine device, the diameters of the third and fourth pistons 25a and 25b are equal to or smaller than the diameters of the first and second pistons 24a and 24b.

  In the supercharging mechanism configured as described above, the fuel / air mixture supplied from the carburetor 120 to the third and fourth cylinders 23a and 23b is pressurized and compressed by the third and fourth pistons 25a and 25b. After that, the exhaust pipe 130 is exhausted. The compressed air-fuel mixture is cooled by the intercooler 124 and further temporarily held in the accumulation chamber 126, and then supplied to the combustion chambers of the upper first and second cylinders 22a and 22b through the exhaust pipe 130 and the air supply port. .

(Second modification)
Next, a supercharging mechanism according to a second modification suitable for a four-cycle engine device will be described. The same reference numerals are given to the same parts as those in the first modification described above, and detailed description thereof will be omitted, and description will be made centering on parts different from the first modification.
FIG. 25 is a diagram schematically showing a supercharging mechanism according to a second modification.

  According to the second modification, in the exhaust pipe 130 of the supercharging mechanism, the control air flow meter 132, the throttle 134, and the fuel injector 136 are arranged in this order between the accumulation chamber 126 and the first and second cylinders 22a and 22b. Is provided. In addition, an air supply pipe 131 is connected to the intake ports of the lower second and third cylinders 23a and 23b, and a throttle 134 is provided in each air supply pipe 131.

  In the supercharging mechanism configured as described above, the air supplied to the third and fourth cylinders 23a and 23b through the throttle 134 is pressurized and compressed by the third and fourth pistons 25a and 25b, and then the exhaust pipe. Exhaust to 130. The compressed air is cooled by the intercooler 124, and further temporarily held in the accumulation chamber 126, then passes through the air flow meter 132 and the throttle 134, and the combustion chambers of the upper first and second cylinders 22 a and 22 b from the air supply port. To be supplied. At that time, fuel is injected into the compressed air by the injector 136, and an air-fuel mixture of the compressed air and the fuel is supplied to the combustion chamber.

  According to the supercharging mechanism according to the first and second modifications configured as described above, the air pressurized and compressed by the third and fourth pistons is supplied to the upper combustion chamber together with the fuel. Thus, combustion efficiency can be improved. The supercharging mechanism according to the first modification and the second modification can be applied not only to the 4-cycle turbo engine device but also to a 2-cycle engine device, a diesel engine, or the like.

  The present invention is not limited to the above-described embodiment or modification as it is, and can be embodied by modifying the components without departing from the scope of the invention in the implementation stage. In addition, various inventions can be formed by appropriately combining a plurality of components disclosed in the embodiment. For example, some components may be deleted from all the components shown in the embodiment. Furthermore, constituent elements over different embodiments may be appropriately combined.

12a ... 1st crankshaft, 12b ... 2nd crankshaft, 20a ... 1st drive unit,
20b ... 2nd drive unit, 22a ... 1st cylinder, 22b ... 2nd cylinder,
23a ... 3rd cylinder, 23b ... 4th cylinder, 24a ... 1st piston,
24b ... 2nd piston, 25a ... 3rd piston, 25b ... 4th piston,
30a ... 1st XY separation crank mechanism, 30b ... 2nd XY separation crank mechanism,
32a ... 1st support member, 32b ... 2nd support member, 50 ... Connection synchronous mechanism,
80a ... 1st drive motor, 80b ... 2nd drive motor, 112 ... Exhaust flow path,
130 ... Exhaust piping

Claims (17)

A first cylinder provided in a first installation plane located on one side of the center reference plane, and a first cylinder provided in the first cylinder so as to reciprocate along a first direction in the first installation plane. A piston, a first crankshaft extending orthogonally to the first installation plane, and a reciprocating motion of the first piston provided between the first piston and the first crankshaft in the first installation plane; And a first XY separation crank mechanism that mutually converts the rotational motion of the first crankshaft,
A second cylinder provided in a second installation plane located opposite to the center reference plane and symmetrically with respect to the first installation plane with respect to the center reference plane; and in the second installation plane, A second piston provided in the second cylinder so as to freely reciprocate along a second direction symmetrical to the first direction, a second crankshaft extending perpendicular to the second installation plane, and the second installation A second XY separation crank mechanism that is provided between the second piston and the second crankshaft in a plane and converts the reciprocating motion of the second piston and the rotational motion of the second crankshaft to each other;
Connecting the one end portion of the one end portion and the second crank shaft of the first crank shaft, a connecting synchronization mechanism for reverse rotation in synchronization with the first crankshaft and the second crankshaft, the two cylinders provided with a A drive device comprising :
The first XY separation crank mechanism is a first support member provided to be reciprocally movable in the first direction, the first support portion extending in the first direction, and the first installation from the first support portion. A second support portion extending in a third direction orthogonal to the first direction in a plane, and a third portion extending from the first support portion along the third direction and facing the second support portion with a gap therebetween. A first support member having a support portion; and between the second support portion and the third support portion of the first support member so as to be reciprocally movable along the third direction within the first installation plane. And a first crank connecting member that is rotatably engaged with a crank pin of the first crankshaft, and a first connecting member that connects the first piston and the first support member. ,
The second XY separation crank mechanism is a second support member provided to be reciprocally movable in the second direction, and includes a first support portion extending in the second direction, and the second installation from the first support portion. A second support portion extending in a fourth direction orthogonal to the second direction in a plane, and a third support portion extending from the first support portion along the fourth direction and facing the second support portion with a gap. A second support member having a support portion, and between the second support portion and the third support portion of the second support member so as to be reciprocally movable along the fourth direction in the second installation plane. And a second crank connecting member that is rotatably engaged with a crank pin of the second crank shaft, and a second connecting member that connects the second piston and the second support member. ,
Each of the first crank connecting member and the second crank connecting member includes a first sliding portion supported by the second supporting portion so as to be reciprocally movable along the third direction or the fourth direction, A second sliding portion supported by the three supporting portions so as to be reciprocally movable along the third direction or the fourth direction, and extending in a direction perpendicular to the first direction and the second direction, and the first crankshaft Or a through hole through which the crank of the second crankshaft is rotatably inserted,
The first connecting member including the first sliding portion and the second connecting member including the second sliding portion are divided by a dividing surface passing through the central axis of the through hole and orthogonal to the first direction or the second direction. The dividing surfaces of the first and second connection members are formed in an uneven surface shape having recesses and protrusions aligned in the axial direction of the through hole, and the first connection member and the second connection member are engage abutted the divided faces attached to the crank pin,
The first piston and the first XY separation crank mechanism operate in synchronization with each other while maintaining a state symmetric with the second piston and the second XY separation crank mechanism with respect to the center reference plane,
The first driven body connected to the first crankshaft is driven to rotate by the first crankshaft, and the second driven body connected to the second crankshaft is driven to rotate reversely by the second crankshaft. Two cylinder drive. A first drive unit including the first crankshaft and provided on one side of the center reference plane, and a second crankshaft, having the same configuration as the first drive unit, on the opposite side of the center reference plane a second driving unit arranged on the first drive unit and symmetrically with respect to said central reference plane, and connects the one end of the second crank shaft and one end portion of the first crankshaft, the first crank in synchronization with the shaft and the second crank shaft to a driving device of two cylinders that example Bei and a coupling synchronous mechanism for rotating in opposite directions,
The first drive unit includes a first cylinder, a first piston provided in the first cylinder so as to be capable of reciprocating along a first direction, and a movement axis of the first piston along the first direction. A first crankshaft extending perpendicularly to a first installation plane including the first piston, and a reciprocating motion of the first piston provided between the first piston and the first crankshaft in the first installation plane. A first XY separation crank mechanism that mutually converts the rotational movement of the first crankshaft,
The second drive unit includes a second cylinder, a second piston provided in the second cylinder so as to be capable of reciprocating along a second direction symmetrical to the first direction with respect to the center reference plane, The second crankshaft extending perpendicular to a second installation plane including a movement axis of the second piston along the second direction and positioned symmetrically to the first installation plane with respect to the center reference plane; A second XY separation crank mechanism that is provided between the second piston and the second crankshaft in a second installation plane and mutually converts the reciprocating motion of the second piston and the rotational motion of the second crankshaft. And comprising
The first XY separation crank mechanism is a first support member provided to be reciprocally movable in the first direction, the first support portion extending in the first direction, and the first installation from the first support portion. a second support portion extending in a third direction perpendicular to the first direction in a plane, a first support member having a reciprocating movably the first along the said third direction in a first installation plane A first crank connecting member that is attached to the support member and in which a crank pin of the first crankshaft is rotatably engaged; and a first connection member that connects the first piston and the first support member; With
The second XY separation crank mechanism includes a second support member provided so as to freely reciprocate in the second direction, a first support portion extending in the second direction, and the second installation plane from the first support portion. A second support member having a second support portion extending in a fourth direction orthogonal to the second direction, and the second support reciprocally movable along the fourth direction within the second installation plane. A second crank connecting member that is attached to the member and is rotatably engaged with a crank pin of the second crankshaft; a second connecting member that connects the second piston and the second support member; wherein the second support member, said second crank connecting member, and the second coupling member, to the central reference plane, said first support member of the first 1XY separation crank mechanism, wherein the first crank connected Member and said first Respectively forming member is formed and arranged symmetrically, while maintaining the symmetrical condition, respectively, and operate in synchronization with each other,
The first driven body connected to the first crankshaft is driven to rotate by the first crankshaft, and the second driven body connected to the second crankshaft is driven to rotate reversely by the second crankshaft. Two cylinder drive. A first cylinder provided in a first installation plane located on one side of the center reference plane, and a first cylinder provided in the first cylinder so as to reciprocate along a first direction in the first installation plane. A piston, a first crankshaft extending orthogonally to the first installation plane, and a reciprocating motion of the first piston provided between the first piston and the first crankshaft in the first installation plane; And a first XY separation crank mechanism that mutually converts the rotational motion of the first crankshaft,
A second cylinder provided in a second installation plane located opposite to the center reference plane and symmetrically with respect to the first installation plane with respect to the center reference plane; and in the second installation plane, A second piston provided in the second cylinder so as to freely reciprocate along a second direction symmetrical to the first direction, a second crankshaft extending perpendicular to the second installation plane, and the second installation A second XY separation crank mechanism that is provided between the second piston and the second crankshaft in a plane and converts the reciprocating motion of the second piston and the rotational motion of the second crankshaft to each other;
Connecting the one end of the second crank shaft and one end portion of the first crank shaft, a connecting synchronization mechanism for reverse rotation in synchronization with the first crankshaft and the second crankshaft,
A first motor connected to the first crankshaft for rotationally driving the first crankshaft;
A two-cylinder driving device comprising: a second motor connected to the second crankshaft and configured to rotate the second crankshaft in a direction opposite to the first crankshaft ;
The first XY separation crank mechanism is a first support member provided to be reciprocally movable in the first direction, the first support portion extending in the first direction, and the first installation from the first support portion. A second support portion extending in a third direction orthogonal to the first direction in a plane, and a third portion extending from the first support portion along the third direction and facing the second support portion with a gap therebetween. A first support member having a support portion; and between the second support portion and the third support portion of the first support member so as to be reciprocally movable along the third direction within the first installation plane. And a first crank connecting member that is rotatably engaged with a crank pin of the first crankshaft, and a first connecting member that connects the first piston and the first support member. ,
The second XY separation crank mechanism is a second support member provided to be reciprocally movable in the second direction, and includes a first support portion extending in the second direction, and the second installation from the first support portion. A second support portion extending in a fourth direction orthogonal to the second direction in a plane, and a third support portion extending from the first support portion along the fourth direction and facing the second support portion with a gap. A second support member having a support portion, and between the second support portion and the third support portion of the second support member so as to be reciprocally movable along the fourth direction in the second installation plane. And a second crank connecting member that is rotatably engaged with a crank pin of the second crank shaft, and a second connecting member that connects the second piston and the second support member. ,
Each of the first crank connecting member and the second crank connecting member includes a first sliding portion supported by the second supporting portion so as to be reciprocally movable along the third direction or the fourth direction, A second sliding portion supported by the three supporting portions so as to be reciprocally movable along the third direction or the fourth direction, and extending in a direction perpendicular to the first direction and the second direction, and the first crankshaft Or a through hole through which the crank of the second crankshaft is rotatably inserted,
The first connecting member including the first sliding portion and the second connecting member including the second sliding portion are divided by a dividing surface passing through the central axis of the through hole and orthogonal to the first direction or the second direction. The dividing surfaces of the first and second connection members are formed in an uneven surface shape having recesses and protrusions aligned in the axial direction of the through hole, and the first connection member and the second connection member are engage abutted the divided faces attached to the crank pin,
The first piston and the first XY separation crank mechanism are two-cylinders that operate in synchronization with each other while maintaining symmetry with the second piston and the second XY separation crank mechanism with respect to the center reference plane. Drive device. A first drive unit including the first crankshaft and provided on one side of the center reference plane, and a second crankshaft, having the same configuration as the first drive unit, on the opposite side of the center reference plane a second driving unit arranged on the first drive unit and symmetrically with respect to said central reference plane, and connects the one end of the second crank shaft and one end portion of the first crankshaft, the first crank A coupling synchronization mechanism for synchronizing and rotating the shaft and the second crankshaft in opposite directions, a first motor connected to the first crankshaft for rotationally driving the first crankshaft, and connected to the second crankshaft And a second motor that rotates the second crankshaft in a direction opposite to the first crankshaft .
The first drive unit includes a first cylinder, a first piston provided in the first cylinder so as to be capable of reciprocating along a first direction, and a movement axis of the first piston along the first direction. A first crankshaft extending perpendicularly to a first installation plane including the first piston, and a reciprocating motion of the first piston provided between the first piston and the first crankshaft in the first installation plane. A first XY separation crank mechanism that mutually converts the rotational movement of the first crankshaft,
The second drive unit includes a second cylinder, a second piston provided in the second cylinder so as to be capable of reciprocating along a second direction symmetrical to the first direction with respect to the center reference plane, The second crankshaft extending perpendicular to a second installation plane including a movement axis of the second piston along the second direction and positioned symmetrically to the first installation plane with respect to the center reference plane; A second XY separation crank mechanism that is provided between the second piston and the second crankshaft in a second installation plane and mutually converts the reciprocating motion of the second piston and the rotational motion of the second crankshaft. And comprising
The first XY separation crank mechanism is a first support member provided to be reciprocally movable in the first direction, the first support portion extending in the first direction, and the first installation from the first support portion. a second support portion extending in a third direction perpendicular to the first direction in a plane, a first support member having a reciprocating movably the first along the said third direction in a first installation plane A first crank connecting member that is attached to the support member and in which a crank pin of the first crankshaft is rotatably engaged; and a first connection member that connects the first piston and the first support member; With
The second XY separation crank mechanism includes a second support member provided so as to freely reciprocate in the second direction, a first support portion extending in the second direction, and the second installation plane from the first support portion. A second support member having a second support portion extending in a fourth direction orthogonal to the second direction, and the second support reciprocally movable along the fourth direction within the second installation plane. A second crank connecting member that is attached to the member and is rotatably engaged with a crank pin of the second crankshaft; a second connecting member that connects the second piston and the second support member; wherein the second support member, said second crank connecting member, and the second coupling member, to the central reference plane, said first support member of the first 1XY separation crank mechanism, wherein the first crank connected Member and said first Binding member and formed and arranged respectively symmetrically, while each maintaining a symmetrical state, the two cylinders operating in synchronization with each other driving device. The drive device according to any one of claims 1 to 4, wherein the first crankshaft and the second crankshaft are arranged in parallel to each other. Said first and second directions, said central reference plane and orthogonal, and the drive device according to claim 1 which extends coaxially to any one of 4 to each other. Wherein the first and second directions, with and forms a smaller angle than 180 degrees, the driving device according to any one of the central reference plane of the claims 1 to cross each other 4. It said first and second directions, the driving device according to any one of the central reference plane parallel to the extending and claims 1 to 4. The first piston is formed in a non-circular shape including an oval shape having a major axis and a minor axis perpendicular to the first direction, and the second piston has a major axis and a minor axis perpendicular to the second direction. drive apparatus according to any one of claims 1 to 8, which is formed in a non-circular shape including oval shaped. The first piston, the long axis is arranged in a direction parallel to the third direction, the second piston, according to claim 9, wherein the long axis is oriented so as to be parallel to the fourth direction The drive device described in 1. The coupling synchronization mechanism includes a first gear, wherein mounted on the one end of the first crank shaft, attached to said one end of said second crank shaft, a second gear meshed with the first gear, The drive device according to any one of claims 1 to 10 , wherein the first gear and the second gear are formed to have the same diameter and the same number of teeth. The connection synchronization mechanism includes a first drive pulley attached to the one end of the first crankshaft, a second drive pulley attached to the one end of the second crankshaft, the first drive pulley, comprising a drive belt looped around the second drive pulley, the drive apparatus according to any one of claims 1 to 10 for reverse rotation in synchronization with each other the first and second crankshaft. A first drive unit including the first crankshaft and provided on one side of the center reference plane, and a second crankshaft, having the same configuration as the first drive unit, on the opposite side of the center reference plane a second driving unit arranged on the first drive unit and symmetrically with respect to said central reference plane, and connects the one end portion of the one end portion and a second crankshaft of the first crankshaft, the first crank shaft And a coupling synchronization mechanism that rotates the second crankshaft synchronously,
The first drive unit includes a first cylinder, a first piston provided in the first cylinder so as to be capable of reciprocating along a first direction, and a third cylinder provided coaxially with the first cylinder. And a third piston provided in the third cylinder so as to reciprocate along the first direction, and provided between the first piston and the third piston, and the first piston of the first piston. A first crankshaft extending orthogonally to a first installation plane including a moving axis along a direction; and provided between the first piston, the third piston, and the first crankshaft in the first installation plane. A first XY separation crank mechanism that mutually converts the reciprocating motion of the first piston and the third piston and the rotational motion of the first crankshaft, and the first and third cylinders, The first XY Comprising a crank case housing a release crank mechanism, a,
The second drive unit includes a second cylinder, a second piston provided in the second cylinder so as to be capable of reciprocating along a second direction symmetrical to the first direction with respect to the center reference plane, A fourth cylinder provided coaxially with the second cylinder, a fourth piston provided in the fourth cylinder so as to be capable of reciprocating along the second direction, the second piston and the fourth piston; The second crankshaft extending perpendicularly to a second installation plane including a moving axis along the second direction of the second piston, the second piston in the second installation plane, and fourth provided between the piston and said second crankshaft, and the 2XY separation crank mechanism for converting a rotary motion of the reciprocating motion and the second crank shaft of the second piston and the fourth piston each other, the 2nd cylinder Provided between the fourth cylinder, and a crankcase that houses the first 2XY separation crank mechanism,
The first XY separation crank mechanism is reciprocally movable along a first support member provided to be reciprocally movable in the first direction and a third direction orthogonal to the first direction in the first installation plane. A first crank connecting member, which is attached to the first support member and in which a crank pin of the first crankshaft is rotatably engaged, and is connected to the first piston and the first support member. A connection member, and a third connection member that connects the third piston and the first support member,
The second XY separation crank mechanism is reciprocally movable along a second support member provided to be reciprocally movable in the second direction and a fourth direction orthogonal to the second direction in the second installation plane. A second crank connecting member that is attached to the second support member and that is rotatably engaged with a crank pin of the second crankshaft, and a second piston that connects the second piston and the second support member. And a fourth connecting member connecting the fourth piston and the second supporting member, the second supporting member, the second crank connecting member, the second connecting member, and the fourth The connecting member is formed symmetrically with respect to the center reference plane, respectively, with the first support member, the first crank connecting member, the first connecting member, and the third connecting member of the first XY separation crank mechanism. It is location, while maintaining the symmetrical condition, respectively, operate in synchronization with each other driving device.   An exhaust passage for supplying pressurized gas compressed in the third and fourth cylinders and exhausted from the third and fourth cylinders to an intake side of the first and second cylinders; The drive device according to claim 13. The first support member of the first XY separation crank mechanism includes a first support portion extending in the first direction, a second support portion extending from the first support portion in the third direction within the first installation plane, A third support portion extending from the first support portion along the third direction and facing the second support portion with a gap therebetween, and the first crank connecting member is disposed on the second support portion. A first sliding portion supported reciprocally along the third direction; a second sliding portion supported reciprocally along the third direction by the third support portion; A through hole extending in a direction orthogonal to one direction and through which a crank pin of the first crankshaft is rotatably inserted, wherein the first connection member is connected to the second support portion, and the third connection The member is connected to the third support part,
The second support member of the second XY separation crank mechanism includes a first support portion extending in the second direction, a second support portion extending from the second support portion in the fourth direction, and the fourth direction. A third support portion extending from the first support portion and facing the second support portion with a gap therebetween, and the second crank connecting member extends along the fourth direction to the second support portion. A first sliding portion supported reciprocally, a second sliding portion supported reciprocally along the fourth direction by the third support portion, and a direction orthogonal to the second direction. And a through hole through which a crank pin of the second crankshaft is rotatably inserted. The second connecting member is connected to the second support portion, and the fourth connecting member is the third support portion. The drive device according to claim 13 or 14, wherein the drive device is connected to the drive unit.   Each of the first crank connecting member and the second crank connecting member includes the first sliding portion by a dividing surface passing through the central axis of the through hole and orthogonal to the first direction or the second direction. And a second connecting member including the second sliding portion, and the dividing surfaces of the first and second connecting members are concave and convex surfaces having concave and convex portions that are aligned in the axial direction of the through hole. The drive device according to claim 15, wherein the first connection member and the second connection member are attached to the crank pin and are engaged with each other in a state in which the divided surfaces are abutted with each other.   The drive device according to any one of claims 13 to 16, wherein the third piston and the fourth piston have the same diameter, and have a diameter larger than the diameters of the first piston and the second piston. .

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