WO2008010490A1 - Cycloid reciprocating engine and pump employing this crank mechanism - Google Patents

Abstract

A cycloid reciprocating engine providing a working engine employing a sufficiently practical linear crank mechanism by general improvements including employment of a multi-cylinder and contrivance of its cylinder layout, contrivance of its balancer element, and contrivance of the structure of a crank shaft. The cycloid reciprocating engine (E) is characterized in that a working engine, employing a piston unit (3) integrating a piston (31) and a piston rod (32) and a so-called linear crank for reciprocating the piston rod (31) linearly by regulation planetary gear mechanism (4) for converting movement of the piston into rotary motion, includes a combination of horizontally opposed two-cylinder arrangement as a unit engine (E2), and horizontally opposed four cylinders concatenating two units as a unit component engine (E4) and the engine is constituted of one component or by concatenating a plurality of components.

Description

 Specification

 Cycloid reciprocating engine and pump device using this crank mechanism

 The present invention relates to a so-called linear crank type reciprocating engine, and in particular, in addition to reduction of vibration, reduction of friction loss and reduction of required rigidity of a crankcase, the compactness of the engine. The present invention relates to a cycloid reciprocating engine which has been improved to achieve smooth movement and the like and has been put to practical use, and a pump apparatus using this crank mechanism.

 Background art

 Conventionally, a reciprocating engine and a pump device (including a compressor) using a linear crank mechanism have been proposed. In order to change the reciprocating motion of the piston into a rotational motion by the crank mechanism, the crankshaft is supported by the left and right eccentric crank members, and the planetary gear mechanism is interposed between the crankshaft and the crankcase. The planetary rod is moved in a planetary motion, and the bottom end of the piston rod moves on a straight locus.

 By the way, although such a linear crank mechanism has wide applicability in the fields of output engines, pumps, and compressors, the structure is complicated and large, and it is difficult to perform smooth movement. Its diffusion has hardly progressed.

 However, in this type of linear crank mechanism, the piston rod has a reciprocating linear motion, so that it is possible to avoid favorable thrust between the cylinder and the piston, generation of thrust stress, and low power loss. The point is that the balance of force and torque due to the inertia of the reciprocating mass can be removed, so that vibration can be reduced, and it is easy to make a longer stroke, making it possible to create an engine suitable for stratified combustion, lean combustion, etc. Thus, it can be well evaluated that it has an advantage over conventional reciprocating engines (Patent Document 1).

 Patent Document 1: JP-A-9 125981

 Disclosure of the invention

 Problems to be solved by the invention

[0003] The present invention has been made in view of such a background, and is reduced in size and weight, and has multiple cylinders. We propose an engine that can be fully put to practical use as a real machine by improving the overall layout of the system, its cylinder layout, its balancer elements, and its output output layout. The name of the present invention is “cycloidal reciprocating engine” because the movement of the linear crank mechanism is a cycloid motion. Means for solving the problem

 [0004] A cycloid reciprocating engine according to claim 1 includes a piston unit including an opposing piston that reciprocates in a cylinder, a piston rod that is integrated with the piston and extends to a crankcase, and rotational movement of the piston. And a stationary planetary gear mechanism having a pitch circle diameter of 4e in the regulating planetary gear mechanism is fixed to the crankcase, while a cranking gear mechanism is interposed between the crankshaft and the piston unit. The rotation eccentric disk with an eccentricity e including a planetary gear with a pitch circle diameter of 2 e is coaxially arranged with the crank pin on the crankshaft so that the center of the planetary gear can rotate, and the rotation eccentric disk is placed at the lower end of the piston rod. In an engine that reciprocally moves the piston unit linearly with a stroke 4e by being combined freely,

 The engine is a unit engine with a combination of two cylinders arranged horizontally facing each other, and a unit component engine consisting of two unit unit engines connected in series to form four cylinders opposed horizontally. One or a plurality of components are connected to each other, and the pistons facing each unit engine are configured to share a mouth end.

 Further, the unit angle of the unit engine in the unit component engine is characterized by 180.degree.

 [0005] In addition to the requirements of claim 1, the cycloid reciprocating engine according to claim 2 is configured such that the unit component engine is connected to other members at an integral structure portion of a crankshaft positioned between the unit unit engines. It is characterized by being configured to transmit power.

[0006] In addition to the requirements described in claim 1 or 2, the cycloid reciprocating engine according to claim 3 is such that the piston has a flat head shape with a short crankshaft direction. It is characterized by this. [0007] The cycloid reciprocating engine according to claim 4 includes, in addition to the requirements according to claim 1, 2 or 3, any two elements of the piston unit, the crankshaft, and the cylinder, or all of them. Between elements, it is characterized by having a linear motion error tolerance structure that corresponds to and allows the linear motion error of the piston unit.

 [0008] In addition to the requirements of claim 4, the cycloid reciprocating engine according to claim 5 has sufficient clearance between the piston unit and the cylinder with respect to the linear motion error allowable structure. It consists of

 [0009] In addition to the requirements of claim 4, the cycloid reciprocating engine according to claim 6 is configured such that the rotational eccentricity disk of the restriction planetary gear mechanism is It is characterized by being mounted via a movable block provided with a slight operating clearance in a direction perpendicular to the cylinder sliding direction.

 [0010] In addition to the requirements of claim 4, the cycloid reciprocating engine according to claim 7 is configured so that the rod end of the piston unit is divided into two parts, and the piston unit as a whole has a rod end. It is characterized by being configured to be slightly refractable at the border.

 [0011] In addition to the requirements described in claim 1, 2, 3, 4, 5 or 6, the cycloid reciprocating engine according to claim 8 is integrated with each opposing piston in the unit unit engine as an opposing piston. It is characterized by being formed.

 [0012] The cycloid reciprocating engine according to claim 9 is the claim 1, 2, 3, 4, 5, 6, 7 or

 In addition to the requirements described in 8, the crank web of the cycloidal reciprocating engine is characterized in that it is supported by a crankcase on its peripheral surface.

 [0013] A cycloid reciprocating engine according to claim 10 is characterized in that, in addition to the requirement according to claim 1, 2, 3, 4, 5, 6, 7, 8 or 9, the unit component engine is = 1, 2, 3, ···) When the base combination is configured as a horizontally opposed 4-cylinder cylinder, the connecting parts of the crankshaft between the unit component engines are connected to each other in the unit component engine connection part. The crankshaft has a predetermined phase difference (180 ° ΖΝ).

[0014] The cycloid reciprocating engine according to claim 11 is characterized in that the claim 1, 2, 3, 4, 5, 6, 7, 8, In addition to the requirements described in 9 or 10, the transmission shaft of the cycloidal reciprocating engine is characterized in that those taken out from each unit component engine are connected together.

[0015] A cycloid reciprocating engine according to claim 12 is the horizontal axis represented by the N = l in addition to the requirement according to claim 1, 2, 3, 4, 5, 6, 7, 8 or 9. In the case of the opposed 4-cylinder configuration, the reciprocating mass inertial force and the inertia torque are unbalanced, leaving only the crank torque due to the reciprocating mass inertia as an unbalancer, and divided by each piston and cylinder. It is characterized in that it is configured so as to be balanced dynamically by smoothing the crank torque generated by the expansion force generated in the working chamber.

[0016] The cycloid reciprocating engine according to claim 13 is characterized in that the claim 1, 2, 3, 4, 5, 6, 7, 8, 9,

 In addition to the requirements described in 10 or 11, the inertial force of the reciprocating mass and the unbalance of the inertial torque in the case of the horizontally opposed 8-cylinder configuration indicated by N = 2 are as follows. In addition to arranging each crankshaft at a predetermined phase angle difference (180 ° / N, N = 2), end balancers are provided at both ends of the crankshaft, and cranks located at the center of each unit engine It is characterized in that it is configured so as to be dynamically balanced by a transmission shaft counter balancer that transmits power to the outside at the center of the shaft.

 [0017] The cycloid reciprocating engine according to claim 14 is characterized in that the claim 1, 2, 3, 4, 5, 6, 7, 8,

 In addition to the requirements described in 9, 10 or 11, in the case of a cylinder configuration of 12 or more horizontally opposed cylinders represented by N≥3, the inertia force of the reciprocating mass and the unbalance of the inertia torque are as follows: When connecting the unit component engines, the crankshafts are arranged in a predetermined phase angle difference (180 ° / N, N = 3, 4, ···) so that they are balanced dynamically. It is characterized by being.

 [0018] The cycloid reciprocating engine according to claim 15 is characterized in that the claim 1, 2, 3, 4, 5, 6, 7, 8,

 It is characterized in that the configuration described in 9, 10, 11, 12, 13 or 14 is applied to a 4-cycle engine.

[0019] The cycloid reciprocating engine according to claim 16, wherein the reciprocating engine according to claim 1, 2, 3, 4, 5, 6, 7, 8, It is a special number that the configuration described in 9, 10, 11, 12, 13, or 14 is applied to a two-cycle engine.

[0020] The pump device according to claim 17 is used in the cycloid reciprocating engine according to claim 1, 2, 3, 4, 5, 6, 7, 8, 9, 10, 11, 12, 13 or 14. It is characterized by the use of a crank mechanism.

 The invention's effect

 [0021] According to the invention of claim 1, since the lower end side of the piston rod moves back and forth along the center line of the cylinder hole, the force received by the piston can be efficiently converted into rotational motion, and more conventionally. As compared with the one using the crank mechanism, cylinder side pressure is not generated, so that the rigidity of the cylinder, the crankcase and the piston unit can be reduced.

 [0022] According to the invention of claim 2, since the power transmission part is an integral part of the crankshaft, there is almost no so-called twist of the crankshaft, and a well-balanced engine can be obtained.

 [0023] According to the invention of claim 3, the cylinder interval can be designed to be narrow, and the length of the piston unit can be shortened when the stroke is the same as compared with the circular piston type. The size in the cylinder direction (engine height) can also be reduced, and the overall engine can be compact. In particular, since the length in the direction of the crankshaft can be shortened, twisting of the crankshaft or unbalance occurring in the crankshaft can be avoided more reasonably. Furthermore, the flat piston head is suitable for absorbing the slight shaking of the center of the rotating eccentric disk in the direction perpendicular to the crankshaft. Furthermore, the piston unit having a flat piston head can be formed into a flat plate shape as a whole, and even if manufactured by a method such as light alloy forging, it is easy to manufacture and can be easily downsized. Can be achieved.

 [0024] According to the invention described in claim 4, 5, 6 or 7, even when an operation error of the crank mechanism, backlash, or switching of the direction of power input occurs, the crank and the crankshaft together with it. Smooth movement of the moving piston unit can be ensured.

[0025] According to the invention of claim 8, since the pair of opposed pistons and the piston rod connected thereto are integrally formed, it is possible to maintain sufficient piston rigidity while achieving weight reduction. In addition, the link part that connects the piston and piston rod can be eliminated, so that power loss can be avoided and stable reciprocation is possible. [0026] Further, according to the invention described in claim 9, when the crankshaft is supported by the crankcase, the bearing is newly provided on the crankshaft at the outer end of the crankweb as in the prior art. It is no longer necessary to provide the engine, and the dimension in the longitudinal direction of the crankshaft can be shortened, and the engine itself can be made compact.

 [0027] According to the invention of claim 10, by connecting two or more unit component engines, the output performance and the like can be improved while being compact.

 [0028] Further, according to the invention described in claim 11, it is possible to adopt a configuration in which the power of the integral structure of the crankshaft of each unit component engine is also extracted to the transmission shaft, and the smooth movement of the transmission mechanism, Furthermore, the function as a balancer is efficiently exhibited, and the vibration and noise of the engine can be reduced.

 [0029] Further, according to the invention of claim 12, 13 or 14, since a plurality of balancer mechanisms are provided for imbalance, each balancer acts in a complex manner and vibrates during operation. Noise and the like can be reduced. Especially in the case of 12 or more horizontally opposed cylinders represented by N = 3 or more, the difference in phase angle between unit units is set to a predetermined value to eliminate unbalanced reciprocating mass and reduce vibration. can do.

 [0030] According to the invention of claim 15 or 16, the force received by the piston can be efficiently converted into a rotational motion, and the piston unit reciprocates while taking a linear locus, whereby the piston The loss due to friction between the cylinder and the cylinder surface can be reduced and the thermal efficiency can be increased.

 [0031] According to the invention of claim 17, it is possible to reduce vibration and noise of a pump and a compressor that are often used continuously regardless of day and night.

 Brief Description of Drawings

 FIG. 1 is a perspective view and a cross-sectional view showing a horizontally opposed four-cylinder cycloid reciprocating engine according to the present invention.

 FIG. 2 is a transverse sectional view showing a horizontally opposed four-cylinder cycloid reciprocating engine according to the present invention.

 FIG. 3 is a longitudinal sectional view showing a horizontally opposed four-cylinder cycloid reciprocating engine according to the present invention.

FIG. 4 is a perspective view showing a part of a piston unit and a crankshaft used in a horizontally opposed cycloidal reciprocating engine according to the present invention, and an embodiment including an example of a linear motion tolerance structure It is.

5] A longitudinal sectional view showing the positional relationship among the piston unit, crankshaft and transmission shaft used in the horizontally opposed cycloidal reciprocating engine according to the present invention, comprising an example of a linear motion error tolerance structure. This is an example.

6] It is an explanatory view of the balance of inertia force and torque of the reciprocating mass of the horizontally opposed 4-cylinder cycloid reciprocating engine according to the present invention.

 [Fig. 7] Fig. 7 is a transverse sectional view and an explanatory diagram of the return mass of the horizontally opposed 8-cylinder cycloid reciprocating engine according to the present invention.

 FIG. 8 is a longitudinal sectional view showing a horizontally opposed 8-cylinder cycloid reciprocating engine according to the present invention. FIG. 9] A longitudinal sectional view showing the positional relationship among a piston unit, a crankshaft, and a transmission shaft used in a horizontally opposed 8-cylinder cycloid reciprocating engine according to the present invention.

FIG. 10] An explanatory diagram of the balance of inertia force and torque of the reciprocating mass of the horizontally opposed 8-cylinder cycloid reciprocating engine according to the present invention.

 FIG. 11 is a cross-sectional view showing a horizontally opposed 12-cylinder cycloid reciprocating engine according to the present invention and an explanatory diagram of reciprocating mass.

12] A longitudinal sectional view showing a horizontally opposed 12-cylinder cycloid reciprocating engine according to the present invention.

FIG. 13 is a longitudinal sectional view showing the positional relationship among a piston unit, a crankshaft and a transmission shaft used in a horizontally opposed 12-cylinder cycloid reciprocating engine according to the present invention.

14] It is an explanatory diagram of the balance of inertia force and torque of the reciprocating mass of the horizontally opposed 12-cylinder cycloid reciprocating engine according to the present invention.

15] A conceptual diagram showing a cycloid reciprocating engine of the present invention, where (1) shows a 4-cycle engine and (2) shows a 2-cycle engine.

16] It is a conceptual diagram showing a crank mechanism of a cycloid reciprocating engine of the present invention applied to a pump or a compressor.

FIG. 17 is a longitudinal sectional view skeletally showing an engine in which a plurality of cycloidal reciprocating engines of the present invention having different crank shafts with respect to a common transmission shaft are arranged.

18] It is explanatory drawing which shows the Example which made the piston head shape flat. 19] This is a cross-section including the crank assembly as above, and also shows a comparison of the width dimensions of the circular piston head type.

FIG. 20] is an exploded perspective view with a focus on a movable member including the crank assembly. 21] FIG. 21 is an exploded perspective view showing an embodiment in which another crank web mechanism (independent type for each unit engine) is further adopted based on the technical idea of the crank assembly section.

 [FIG. 22] A longitudinal section showing another method for allowing a linear motion error, and embodying the basic technical idea of the structure for allowing a linear motion error.

FIG. 23 is an explanatory diagram showing still another method of the linear motion error allowable structure.

[24] It is a reference example of the technical idea of the present invention, and is a three-sided view showing a non-horizontal opposed type engine.

Explanation of symbols

 1 Crankcase

 10a Crank chamber

 10b Working chamber

 11 cylinders

 12 Cylinder head

 13 Center journal bearing

 14 Side journal bearing

 15a Air intake hole

 15b Intake valve

 16a Exhaust hole

 16b Exhaust valve

 17 Sweeping

 2 For crank cars

 21 Crank web

 21A crank web

 21B crank web

21P Crank pin receiving hole 2 Transmission gear

3 Crankpin

3a Crank pin bearing 3P Crank pin insertion part 4 Crank web

5 Crankshaft balancer 6 Connection panel

 Piston unit

F Piston unit element 1 Piston

1a Piston ring

1b Piston skirt

2 Piston rod

21 Thin section

22 Thick part

3 Ϊ 3d, end,

3C circlip

3D split plane

3R retainer ring

4 Rod end bearing 5 Movable block

5a Bearing receiving hole

5c Movable block clear run "5f Minute sliding surface

6 Movable block receiving hole 6f Minute sliding surface

Regulated planetary gear mechanism 1 Rotating eccentric disc 42 Planetary gear

 43 Static ring gear

 5 Transmission mechanism

 51 Transmission shaft

 52 Transmission gear

 55 Transmission shaft balancer

 C Cylinder axis (direction) center line

 1

c Cylinder axis (direction) center line

 2

c Cylinder axis (direction) center line

 Three

c Cylinder axis (direction) center line

 Four

c Cylinder axis (direction) center line

 Five

c Cylinder axis (direction) center line

 6

 Dc Split surface clearance

 E cycloid reciprocating engine

 E2 unit engine

 E4 unit component engine (horizontally opposed 4-cylinder cycle 1-roid reciprocating engine)

E8 Horizontally opposed 8-cylinder cycloid reciprocating engine

 E12 Horizontally opposed 12-cylinder cycloid reciprocating engine

 E Axial center point of rotation eccentric disc axis

 1

 E Axial center point of rotation eccentric disc axis

 2

 E Axial center point of rotation eccentric disc axis

 Three

 E Axial center point of rotation eccentric disc axis

 Four

 E Axial center point of rotation eccentric disc axis

 Five

 E Axial center point of rotation eccentric disc axis

 6

s Oino Resino

 P Spark plug

 Pc Piston clearance

o Origin (center of crankshaft) o For crank cars,

 1

 o Crank pin axis

 2

 O Spindle eccentric disc axis

 Three

 〇 Transmission shaft center

 Five

 w Cylinder real width (of circular piston head)

 0

 w Cylinder real width (of flat piston head)

 1

 BEST MODE FOR CARRYING OUT THE INVENTION

 The best example of the present invention is disclosed in the following description of specific embodiments and drawings.

 Regarding the cycloid reciprocating engine of the present invention shown in FIGS. 1, 2 and 7, etc., a valve corresponding to the specification mode is not written in the cylinder head part. As shown in FIG. 15, at least one set of an intake valve and an exhaust valve is provided. Of course, it is also possible to use a multi-valve type in which a plurality of these intake valves and exhaust valves are provided. Further, since these techniques are already well known, detailed explanations thereof are omitted.

 Example 1

 [0035] The cycloidal reciprocating engine E of the present invention is configured by combining N (N = 1, 2, 3,...) Units component engines E4 having two unit unit engines E2. It is. The number attached to the symbol E is based on the number of cylinders. For example, the symbol E8 described later indicates that eight cylinders are provided in total.

 First, the basic unit engine unit E2 is roughly divided into a crankcase 1, a crankshaft 2 supported by the crankcase 1, a piston unit 3 reciprocating in a cylinder 11 attached to the crankcase 1, and the piston. The control planetary gear mechanism 4 interposed between the unit 3 and the crankshaft 2 is a main member.

 The cycloid reciprocating engine E of the first embodiment shown in FIG. 1 and the like has a single unit component engine E4 according to claim 1, and therefore the cylinder 11 is arranged horizontally. Cylinder.

[0036] Next, explanation will be given on each member constituting. First, as shown in FIGS. 1 and 2, the crankcase 1 is constituted by die casting having an appropriate strength, and the crankcase 1 is a separate cylinder so as to protrude further to the side. As an example, 4 units are installed, and a cylinder head 12 is attached to each.

 Further, the crankcase 1 is provided with a center journal bearing 13 as a bearing member in the center thereof, and a side journal bearing 14 near the front and rear outside thereof. Of course, the explanation of the arrangement position of the side journal bearing 14 is For example, when the cycloid reciprocating engine E is used in an automobile, a motorcycle, etc., the longitudinal direction of the crankshaft 2 to be described later depends on the longitudinal direction of the automobile. Needless to say, it may be more appropriate to express it as side.

 Next, explanation will be given on the crankshaft 2 that is rotatably supported by such a crankcase 1. First, the crankshaft 2 is supported by the center journal bearing 13 in a crank web 21 that also functions as a crank boss in a conventional engine as shown in the figure, and the crank web 21 is transmitted to the center thereof. The gear 22 is arranged.

 [0038] Then, a crank pin 23 is formed so as to extend from the crank web 21 force to the base side of the cylinder 11 aligned in the axial direction, and the crank pin 23 is formed at each end of the crank web 24. The side journal bearing 14 provided in the crankcase 1 is rotatably supported. The crank angle of the pair of crank pins 23 is 180 °.

 In addition, the outer side is subjected to an airtight action by the oil seal S. The crankshaft balancer 25 corresponding to the end balancer described in claim 2 is assembled at both ends of the crankshaft 2, and the balancer state is as shown in FIGS. The positions are set so as to face each other at both ends.

Next, the piston unit 3 that is a reciprocating member will be described.

As shown in FIG. 4, the piston unit 3 reciprocates in the cylinder 11, and the piston 31, which is a part of the piston unit 3, is provided with a piston ring 31a on its periphery in order to maintain airtightness. Yeah. A piston rod 32 is formed to extend from the back side of the piston 31, and the rod end 33 at the end thereof is assembled so as to be connected to the regulating planetary gear mechanism 4.

 The rod end 33 and the regulating planetary gear mechanism 4 are assembled to each other through a rod end bearing 34 so as to be rotatable.

[0040] Further, in the piston unit 3, the rod end 33 is commonly attached to the piston rod 32 extending from each of the horizontally opposed pistons 31, and the pistons for the horizontally opposed two cylinders. Unit 3 takes the form of an integrated so-called monoblock. Therefore, the rod end 33 is located in the center of the piston unit 3 as a part shape regardless of its name.

 Of course, a pin-shaped connecting member is interposed between the lower end of the piston 31 and the rod end 33, so that it does not matter.

 A circular hole portion is provided in the portion of the rod end 33, and the rod end bearing 34 is combined with the circular hole portion so as to be fitted thereinto. The rod end bearing 34 is combined so that a rotation eccentric disc 41 described later is fitted therein.

 [0041] Here, with respect to the rod end 33, the force described in claim 1 that the pair of pistons 31 in a horizontally opposed state share the rod end 33 of the piston rod 32. This means that the center of the action position of the rod end 33 is shared. Therefore, the rod end 33 may have a structure that divides this part into two parts, and the rod end 33 is in a shared state. is there.

 Incidentally, the piston unit 3 applied to FIG. 13 has a configuration in which weight reduction can be attempted while maintaining sufficient strength. That is, as shown in the end view in the figure, the upper end portion of the piston 31 and the rod end 33 are formed in a thin plate shape as a whole, and the central portion is thinned in a side view, and the peripheral portion is relatively thin. It has a thick rib shape. Reference numeral 321 in the end view of FIG. 13 indicates a thin portion, and reference numeral 322 indicates a thick portion.

[0042] When pursuing such a compact piston 31 and piston rod 32 and rod end 33 or a reduction in thickness, the piston 31 itself is also as shown in FIGS. The surface shape of the piston head may be flat rather than circular.

 In this embodiment, an oval piston head shape is taken as an example. However, the long side portion of the oval shape or the oval shape may be bulged somewhat outward. Such a configuration is appropriately selected in consideration of the manufacturing accuracy and ease of manufacturing of the piston ring fitted therein. When such a flat piston is employed, the length dimension in the direction of the crankshaft 2 can be significantly reduced even in the assembled state of the engine, that is, in the unit component, as shown in FIG.

 Incidentally, Fig. 19 also shows the length dimension (actual cylinder width W) in the two directions of the crankshaft when a skeleton-shaped piston head with a circular shape is applied.

 0

The length dimension of the unit component engine E4 using tons (actual cylinder width W)

 1

It can be reduced to about 1Z2 compared to the one using a stone. By configuring in this way, the axial unbalance element of the crankshaft 2 can be more concentrated in the center and contribute to the reduction of vibration generating elements.

 Compared with the circular piston type, the length of the piston unit 3 can be shortened when the stroke is the same, so the dimension in the cylinder direction (engine length) can be reduced and the entire engine can be designed in a compact manner. Become.

 Furthermore, the flat piston head is also suitable for absorbing slight fluctuations at the center of the rotating eccentric disk in the direction perpendicular to the crankshaft.

 Further, when viewed as the piston unit 3, it can be formed into a flat plate as a whole, and even if it is manufactured by a method such as light alloy forging, it is easy to achieve downsizing.

In the present embodiment, the rod end bearing 34 described above is directly attached to the rod end 33 portion of the piston unit 3 or may be attached via a movable block 35 as shown in FIG. Yo! As an example, the movable block 35 is a rectangular plate member with four corners, and a bearing receiving hole 35a for fitting the rod end bearing 34 is provided at the center thereof. Is. The movable block 35 is fitted so that the minute sliding surface 35f faces the minute sliding surface 36f of the movable block receiving hole 36 provided in the center of the piston unit 3 with a very small clearance. In the direction perpendicular to the reciprocating direction of the piston unit 3, It is configured to provide a movable block clearance 35c.

 For this reason, the rod end bearing 34 is held with respect to the piston unit 3 so as to be finely movable in a direction perpendicular to the reciprocating direction of the piston 31, so that the piston unit 3 is finely moved in the direction perpendicular to the cylinder. Even when such a force is applied, it is allowed to slide in the cylinder 11 with the allowance. In addition, as such a movement, when this cycloid reciprocating engine E is applied to an automobile or a motorcycle, a movement in a case where reverse torque is generated such that an engine brake is applied can be mentioned.

The configuration provided with the above-described movable block 35 is an example of a linear motion error allowable structure for causing the piston 31 to smoothly reciprocate. , 23 can be adopted. As shown skeletally and exaggeratedly in FIG. 22, if the piston clearance Pc is sufficient for the cylinder and the piston 31 is exaggeratedly speaking, the sliding locus is selected up and down as shown in FIG.22 (c). It may be in the form of obtaining. If configured in this way, the smooth operation allowing the operation error, the change of the torque direction, etc. at the time of power transmission as described above becomes possible.

[0045] (2) Rod end 2 harm ij type

 As another example of the linear motion error allowable structure, as shown in FIG. 23, in the piston unit 3, the rod end 33 part is divided into two by the center line as an example, and two piston unit elements 3F are obtained. A slight dividing surface clearance Dc is provided between the dividing surfaces 33D, and the piston unit 3 as a whole is configured so that it can be somewhat refracted around this intermediate portion. Of course, in a steady operation state, even if the piston unit 3 is divided at the center, the piston unit 3 operates as a unit and must be assembled as a unit. As a configuration for that purpose, in the rod end 33 part, as shown in FIG. 23 (a), a retainer ring 33R that is fitted on both the left and right sides, and a circlip 33C for retaining the retainer ring 33R are fitted. Realizes an integrated assembly configuration.

In the case of this configuration as well, the operation is smoothly performed while allowing an operation error or the like. It is.

 The dividing surface 33D may be on a center line that is inclined perpendicular to the central diameter line that is orthogonal to the longitudinal direction of the piston unit 3, or may be on a center line that is inclined, not on the diameter line, and bends at the center and is divided. Unit element 3F may be asymmetrical.

 In order to understand these embodiment forces, the above-described flat piston type is preferable when considering the linear motion error allowable structure.

Next, the restriction planetary gear mechanism 4 for causing the piston unit 3 to perform linear reciprocation will be described.

 First, the rotating eccentric disc 41 in the regulating planetary gear mechanism 4 is rotatably fitted to the crank pin 23 via a bearing such as a crank pin bearing 23a, and the crank pin 23 is in an eccentric state. The rod end 33 is fitted into the rod end 33 so as to be rotatable through the rod end bearing 34.

 A planetary gear 42 is integrally provided on the side surface of the rotating eccentric disc 41 with the crankpin 23 and the shaft center in common, and the planetary gear 42 is fixed on the inside of the crankcase 1. The planetary movement is carried out by holding inside the ring gear 43.

 In order for the rod end 33 to move linearly mechanically or geometrically, the ratio of the pitch circle diameters of the planetary gear 42 and the stationary ring gear 43 must be 1: 2. The pitch circle diameter of the stationary ring gear 43 is equal to the piston stroke (4e).

Next, the transmission mechanism 5 that meshes with the transmission gear 22 will be described.

 This transmission mechanism 5 is a member that bears a smooth power transmission between the crankshaft 2 and the outside, and balances an inertia torque T about the y-axis generated by the inertia of the reciprocating mass described later.

 y

 It can also be used as a balancer mechanism. As shown in FIG. 5, this is composed of a transmission shaft 51 for transmitting power to both sides, and a transmission gear 52 fixed thereto.

Specifically, in the case of the cycloid reciprocating engine E, power is output to the outside, so that the transmission gear 52 of the transmission mechanism 5 serves as an output gear to transmit power to the outside. In the case of a pump or compressor using the crank mechanism of the moving engine E, it is used as an input gear when external motor power is transmitted to the crankshaft 2. Move.

 [0048] The transmission mechanism 5 including a combination of the transmission gear 22 and the transmission gear 52 includes a crankshaft.

 When viewed in the axial direction of 2, when the unit component engine E4 is used as a reference, it is preferable that the crankshaft 2 is disposed between the body structural parts, that is, between the cylinders 11. As a result, power transmission is achieved at the most rigid part of the crankshaft 2 and an assembly structure is required.In the case of the crankshaft 2, the crankshaft 2 is effectively prevented from being twisted. , In

 However, if this design strength problem has not occurred or has been resolved, power transmission should be attempted at a location other than the integral structure of the crankshaft 2. Specifically, the transmission mechanism 5 may be arranged at both ends of the crankshaft 2 as disclosed in a unit component engine E4 to which the flat piston type shown in FIGS.

 In this case, as for the assembly structure of the crankshaft 2, the central connecting portion (between cylinders) of the unit component engine E4 is an assembly crank, and a crank pin 23 and a crank web 24 at both ends are integrally provided with a transmission gear 22. The transmission shaft 51 is connected by a mating transmission gear 52. Specifically, as understood from the exploded perspective view shown in FIG. 20, this assembly structure is provided with a crank pin receiving hole 21P disposed at 180 ° on the center crank web 21 as a connecting medium, and on the other hand, A crankpin insertion portion 23P is formed at the end of the crankpin 23 that is divided into two, and the crankpin insertion portion 23P is press-fitted into the crankpin receiving hole 21P.

 [0049] If the structure in which the transmission mechanism 5 is not provided in the central crank web 21 is further pursued as described above, the unit unit engine E2 can be configured to be completely independent as shown in FIG. It is. That is, in this case, the central crank web 21 is divided into the applied force and the axial direction, and is composed of two members, the crank web 21A and the crank web 21B. Each crank web 21A, 21B has one crank pin receiving hole 21P for receiving the crank pin 23, and when both the crank webs 21A, 21B are in the assembled state, they are shown in FIG. 21 (b). Thus, each crank pin receiving hole 21P is provided at a position opposed to 180 °.

Incidentally, with such a configuration, the rigidity of the crankshaft 2 can be improved. Also The torsional load on the assembly portion of the crankshaft 2, that is, the crank web 21, is removed, and the crankshaft 2 is prevented from being twisted. In addition, the crankshaft 2 can be easily manufactured and the mechanism can be easily assembled. In addition, it can contribute to the smooth engagement of the planetary gears provided on the left and right

[0050] Further, regarding the transmission gear 52, setting of the gear ratio and the like will be described. The transmission gear 52 meshes with the transmission gear 22 fixed to the crankshaft 2 described above, and the ratio of the number of gear teeth between the transmission gear 52 and the transmission gear 22 is such that the transmission mechanism 5 has a balancer. It depends on whether or not it has a function as a mechanism.

 Specifically, the transmission mechanism 5 is used as a balancer mechanism, which will be described later, and a unit component engine E4, a horizontally opposed 4-cylinder cycloid reciprocating engine E4, and two unit component engines E4 are connected. This is the case of a horizontally opposed 8-cylinder cycloidal reciprocating engine E8. For these, the ratio of the number of gear teeth between the transmission gear 52 and the transmission gear 22 is set to the ratio of the number of teeth of 1: 1.

 Although details will be described later, when the transmission mechanism 5 is not used as a balancer mechanism, specifically, a unit component engine E4 with N≥3 is connected (cycloid reciprocation of horizontally opposed 12 cylinders and 16 or more cylinders). In the engine E), the ratio of the number of gear teeth between the transmission gear 52 and the transmission gear 22 can be arbitrarily set.

 As shown in FIG. 3 and the like, the transmission shaft 51 that supports the transmission gear 52 has two transmission shaft balancers 55 on both sides (front and rear) of the transmission gear 52 for reducing vibration and noise, which will be described later. It is attached. The transmission shaft balancer 55 plays the role of the counter balancer as defined in claim 13.

 [0051] Even in the case of the horizontally opposed 4-cylinder unit component engine E4, it is possible to adopt a structure in which the balancer action is not required in the transmission mechanism 51, particularly the transmission shaft 51, and only a simple power transmission is assumed. As a structure, there is no problem. Of course, the gear ratio is not limited to 1: 1 in this case.

 [0052] What has been described above is an example of a specific structure of the present invention, which operates as follows.

First, when the crankshaft 2 rotates, the crankpin 23 rotates the rotation eccentric disc 41 in the restriction planetary gear mechanism 4. At this time, the planetary gear 42 that rotates together with the planet is a stationary ring gear 4 The piston unit 3 with its rod end 33 fitted on the rotation eccentric disc 41 via the rod end bearing 34 is always centered on the cylinder 11 and the crankshaft 2 Reciprocates on a straight line connecting the two.

[0053] Here, the relationship between the movements of the respective gears will be specifically described. First, when the piston stroke is expressed as 4e, the stationary ring gear 43 having a pitch circle diameter of 4e is fixedly disposed on the crankcase 1 so as to coincide with the crankshaft center 0 as its axis.

 1

 On the other hand, the planetary gear 42 having a pitch circle diameter 2e is rotatably supported by the crankpin 23 via the crankpin bearing 23a, so that it is engaged with the stationary ring gear 43 and centered on the crankpin axis O. As the crankshaft O of the crank radius e

 2

 Revolves around in the opposite direction at the same angular velocity.

 1

 The rotational eccentric shaft center O of the eccentric amount e integrally formed with the planetary gear 42 is the cylinder

 Three

 In the direction of the axis center line C (Hereafter, each unit unit E2 is shown as C force C in the figure)

 1 6

 Stroke 4e linear reciprocating motion, that is, cycloid motion. In addition, since the present invention is a horizontally opposed type cylinder arrangement sharing the mouth end 33, the opposed pistons 31 repeat the compression state and the expansion state.

 For convenience, the inner space on the rod end 33 side of the piston 31 is used as the crank chamber 10a, and the space on the head side of the piston 31 is used as the working chamber 10b.

In such a reciprocating engine, the force that naturally generates vibrations is solved by the following means.

 First, in the cycloid reciprocating engine E of the present invention, since the balancing of the rotating body is well known, a description thereof will be omitted, and a method of balancing the inertial force and inertial torque of the reciprocating mass will be described. The linear reciprocating motion of the piston unit 3 of the cycloidal reciprocating engine E of the present invention is as follows: the angular velocity ω around the crankshaft axis of the crankshaft 2 ω, the crankpin axis of the crankpin 23

 1 2 Crankpin shaft center Ο 'Angular velocity around – created by planetary gear 42 rotating at a constant speed at ω

 2

 This is a so-called cycloid movement.

 Inertial force F generated on the mass 慣 of the reciprocating piston unit 3 around the z axis (crank axis)

 E

The inertia torque T of Y, the inertia torque T around the y axis, and the inertia torque T around the X axis are based on the right-handed orthogonal coordinate system O-xyz as shown in Fig. 6 with the origin at the center of the crankshaft. Described for the coordinate system. The balancer may not be symmetrically arranged with respect to the origin 0, but here, from a practical viewpoint, the apparatus structure including the balancer is symmetric with respect to the origin o. As shown in Fig. 6, the mass M is concentrated at the axial center points E and E of the rotating eccentric disc axis,

 E 1 2

 Balance mass M at both ends of crankshaft 2 and balancer mass M at both ends of transmission shaft 51

 A B

 Get in touch with each other. At this time, the radial distance from the center of rotation of the center of gravity of mass M and M

 A B

 R, R, and the point where the reciprocating mass M is concentrated, the mass M and the center of gravity of M

 A B E A B

 Let d, d, and d be the distances in the rotational axis direction, respectively. Is it a well-known theory of dynamic balancing?

 E A B

 If various quantities are determined so as to satisfy the following relational expressions (1) and (2), the inertial force F of the reciprocating mass, inertia torque T around the X axis (crankshaft center) and y axis The inertia torque T is balanced.

 In the unit component engine E4, that is, the horizontally opposed 4-cylinder cycloidal reciprocating engine E, the crank torque caused by the force applied to the piston 31 such as the combustion chamber explosive force is smoothed. Leave inertia torque T without balancing.

 z

 [0055] [Equation 1]

M _E edE = (MARA JA + MBRBCIBJ ( ₁ )

= MBRBCIB (2) [0056] [Equation 2]

= MBRBCIB (2)

[0057] [Equation 3]

Tz =-2M _E e ² J ² sin26tJt (3) Example 2

 [Horizontally opposed 8-cylinder cycloidal reciprocating engine E8 (4-cycle engine) with N = 2] Next, an example related to the horizontally opposed 8-cylinder cycloidal reciprocating engine E8 in which two unit component engines E4 are connected together will be described. I will explain.

As shown in Fig. 7 and Fig. 8, one crankshaft balancer 25 of each unit component engine E4 is eliminated, and a common crank web-like connecting plate 26 is provided on the end side of the unit, as shown in Figs. Two unit component institutions E4 are connected. Specifically, when connecting the two unit component engines E4, the crankshaft 2 is 90 ° (180 ° / N, N = 2) Connected using the connecting board 26 so that the phases are different.

 As for the transmission mechanism 5, as shown in FIGS. 8 and 9, each transmission gear 52 is connected to a common transmission shaft 51 so as to mesh with the transmission gear 22 provided at the center of each unit component engine E4. Attach to. Furthermore, a transmission shaft balancer 55 for suppressing vibration is attached to the transmission shaft 51.

[0059] Inertial force F generated in the mass M of the piston unit 3 that reciprocates F, z axis (crank axis) rotation

 E

 The inertia torque T, the inertia torque T about the y axis, and the inertia torque T about the X axis are based on the right-handed orthogonal coordinate system O-xyz as shown in Fig. For the quasi-coordinate system. The balancer may not be symmetrically arranged with respect to the origin 0, but here, from a practical point of view, the structure of the apparatus including the balancer is symmetric with respect to the origin 0. As shown in Fig. 10, mass M is the axial center point E, E, E, E

 E 1 2 3 4 Concentrate on both ends of crankshaft 2 and balance weight M on both ends of transmission shaft 51.

 A

 Provide a mass M and balance the movement. At this time, from the center of rotation of the center of gravity of mass M and M

B A B

 , R and R, respectively, and the point where the reciprocating mass M is concentrated, the mass M and

 A B E A

 Let d, d, and d be the distances in the direction of the rotational axis of the center of gravity of M, respectively.

 B E A B

 From the well-known theory of dynamic balancing, the inertial force and inertial torque of the reciprocating mass can be balanced within the mechanism by setting various quantities so as to satisfy the following relational expressions (4) and (5).

[0060] [Equation 4]

_MEedE = ₍₄₎

 [0061] [Equation 5]

 MARACIA = MB BCIB (5)

 Example 3

 [0062] [Horizontally opposed 12-cylinder cycloid reciprocating engine with N = 3 E12 (4-cycle engine)]

Next, a horizontally opposed 12-cylinder cyclone with three unit component engines E4 connected to each other. An embodiment relating to the id reciprocating engine El 2 (4-cycle engine) will be described.

 As shown in Fig. 11, Fig. 12, Fig. 13, etc., the crankshaft balancer of both unit component engines E4 is abolished, and a common crank web-like connecting board 26 is provided at the end side. Thus, three unit component institutions E4 are connected. To explain the specific connection form, when connecting the three unit component engines E4, the crankshaft 2 is noisy and 60 ° (180 ° / N, N = 3) Connected using the connecting board 26 so that the phases are different.

 As for transmission mechanism 5, as shown in FIGS. 13 and 14, each transmission gear 52 is connected to a common transmission shaft so as to mesh with transmission gear 22 provided at the center of each unit component engine E4. Attach to 51. Since the transmission mechanism 5 does not have a function as a balancer mechanism, a transmission shaft balancer for suppressing vibrations at both ends of the transmission shaft 51 is not attached.

 By arranging the unit component engine E4 with a predetermined crank angle phase difference as shown in Fig. 11 ~: 14, the inertial force and inertial torque of the reciprocating mass are balanced inside the mechanism based on the well-known theory of dynamic balancing. be able to. Therefore, since the transmission mechanism 5 does not have a function as a balancer mechanism, the transmission shaft balancer for suppressing vibrations at both ends of the transmission shaft 51 is configured only with a deceleration output shaft that is not attached. ing. Example 4

[Horizontal-opposed 16-cylinder reciprocating engine E (4-cycle engine) with N≥4) (Four-cycle engine) In addition, four or more horizontally-facing 16-cylinder cycloid reciprocating engine E (4 cycles) An embodiment relating to an engine will be described.

 In this case, the imbalance between the back and forth mass inertia force and the inertia torque in the horizontally opposed 16-cylinder cycloid reciprocating engine E (4-cycle engine) is strictly the same as that of the horizontally opposed 4- and 8-cylinder cycloid reciprocating engines E4 and E8. Such as the crankshaft balancer 25 and transmission shaft balancer 55 as appropriate, and the phase difference of the crankshaft is set to 180 ° / N (N = 4, 5, ···) at the connection between the unit component engines E4 It is preferable to eliminate this kinetically.

However, the unbalance is improved by the crankshaft balancer 25 and the transmission shaft balancer 55. Since the balance is very small, there is a restriction by providing these balancer members (for example, the number of teeth of the transmission gear 52 is uniquely determined) and an unbalance by these balancer members. However, from a practical point of view, as with the horizontally opposed 12-cylinder cycloidal reciprocating engine E12, there is a slight imbalance. The imbalance can be improved only by setting the phase difference of. Depending on the value of N, it may be possible to completely cancel the imbalance kinetically only by the method of setting the connecting portion of the crankshaft 2 to a predetermined phase difference as in the case of N = 3. is there.

[0064] Alternatively, a plurality of horizontally opposed n-cylinder cycloid reciprocating engines E with different crankshafts 2 may be configured such that their transmission gears 22 are held together on a common transmission shaft 51. In particular, in the horizontally opposed 12-cylinder reciprocating piston engine E12 described above, since the transmission shaft 51 itself does not have a balancer function, the number of teeth of the transmission gear 52 can be made arbitrary, and different crankshafts 2 It is possible to design each horizontally opposed 12-cylinder reciprocating piston engine E12 equipped with so as not to buffer each other. Specifically, as shown in FIG. 17, the transmission gear 22 is engaged with the common transmission shaft 51 from both the upper and lower sides. The arrangement is such that the transmission shaft 51 is sandwiched. Of course, in addition to being constituted by two cycloid reciprocating engines E, it is also possible to constitute by more cycloid reciprocating engines E.

 Example 5

 [0065] [Cycloid reciprocating engine excluding balancer mechanism]

 As described above, the cycloid reciprocating engine E according to the present invention has a crank according to the configuration of each engine from the viewpoint of dynamics in order to eliminate the imbalance that is the cause of vibration-noise in the operating state. A crankshaft balancer 25 at both ends of the shaft 2 and a transmission shaft balancer 55 at both ends of the transmission shaft 51 are appropriately provided.

However, if the overall properties of the cycloid reciprocating engine E such as the crankshaft rotation speed in use, the relationship between the piston stroke and the piston diameter, the number of cylinders, etc. satisfy certain conditions, It is also possible to omit the balancer. Specifically, the horizontally opposed 4-cylinder cycloid reciprocating engine E4 when N = l and the horizontally opposed 8-cylinder cycloid reciprocating engine E8 when N = 2 are dynamically By eliminating the various required balancers and setting the phase angle when connecting adjacent unit units to a predetermined one, the same quiet operation performance as that provided with the balancer is achieved under certain conditions. It is possible to make it.

[0066] [Reference design example]

 Although the present invention is basically of the horizontally opposed piston type, a part of the configuration can be used to realize a non-horizontal opposed type as shown in FIG.

 For example, the one shown in FIG. 24 is of a flat piston type and has sufficient novelty itself. In addition, about the name of each member, a code | symbol, etc., since it can use in common with the already described Example, detailed description is abbreviate | omitted. A cycloid reciprocating engine E employing such a mechanism can also be expected to be put into practical use.

 Industrial applicability

[0067] The cycloid reciprocating engine E described above can be used as a power source of a transport machine, a power source of a generator, and the like that generate output using fossil fuel or the like. Furthermore, it is also possible to use as a pump device by obtaining power from the outside using the crank mechanism of the cycloid reciprocating engine E. Each operation mode will be described below.

 The pump device used in this specification means a device that continuously lifts, presses, compresses or discharges fluid by mechanical or other means. Both the pump and the compressor are used. Is included.

[0068] [1. When used as an output engine (motor)]

 As shown in FIG. 15 (1), when the cycloid reciprocating engine E of the present invention is applied to a four-stroke engine, the cylinder head 12 is provided with an intake hole 15a and an intake valve 15b for opening and closing the intake hole 15a. Further, an exhaust hole 16a and an exhaust valve 16b for opening and closing the exhaust hole 16a are provided, and a spark plug P is further provided. Of course, in a diesel engine, a fuel injection nozzle is provided instead of the spark plug P.

Of course, in this case, an appropriate valve mechanism can be adopted as the valve operating mechanism. As for the number of supply / exhaust valves, etc., at least two of the exhaust valve 16b and the intake valve 15b are necessary, but it may be a multi-valve type, but the description thereof will be omitted. The rotation output obtained by this is taken out from the transmission gear 22 via the transmission gear 52.

 In addition, when applied to a 4-cycle engine, due to the configuration of this device, cylinder side pressure is not generated, and the force and piston stroke are four times the crank radius, so it is easy to make a so-called long stroke. Accordingly, an engine suitable for stratified combustion and lean combustion can be obtained.

 The same applies when the cycloid reciprocating engine E of the present invention is applied to a two-cycle engine. As shown in Fig. 15 (2), due to the characteristics of the supply / exhaust valve structure, the intake hole 15a opens to the side of the cylinder 11 closer to the crankcase 1, and the crank chamber 10a and the working chamber 10b closer to the crank are connected to the scavenging hole. In addition, the exhaust hole 16 a having a timing earlier than the scavenging hole 17 is opened on the side surface of the cylinder 11.

 The piston 31 includes a piston skirt 31b that extends downward from the head of the piston 31 so as to open and close the exhaust hole 16a and the scavenging hole 17.

 Similarly, in the case of a two-cycle engine, when the crankshaft 2 rotates, when the piston 31 moves up, intake is performed on the crank chamber 10a side and a compression process is started on the working chamber 10b side. The air-fuel mixture in the working chamber 10b is combusted by ignition by the spark plug P, and the piston 31 is lowered again by the energy. First, when the exhaust hole 16a is opened, the internal combustion gas is moved to the exhaust pipe side. leak. At the same time, the scavenging holes 17 allow the fresh air mixture gas compressed on the crankcase 1 side to move to the working chamber 10b side and perform self-scavenging.

[0070] [2. When used for pump equipment (compressor, pump)]

When the crank mechanism of the cycloid reciprocating engine of the present invention is applied to a compressor and a pump, first, power from the outside is obtained through the transmission gear 52 and the crankshaft 2 is rotated as shown in FIG. As a result, the piston 31 reciprocates and sucks or sucks in a desired medium such as gas or liquid from the intake hole 15a in the cylinder 11, and the piston 31 moves up in the next process to compress the desired medium. And is discharged from the exhaust hole 16a. In such a case, a one-way valve is sufficient for the intake valve 15b and the exhaust valve 16b.

S60l790 / .00Zdf / X3d 92 061 ^ 010/800 ^ OAV

Claims

The scope of the claims  [1] A piston unit including an opposing piston that reciprocates in a cylinder, a piston rod that is integrated with the piston and extends to a crankcase, a crankshaft that changes the movement of the piston into a rotational motion, and the crankshaft A stationary planetary gear having a pitch circle diameter of 4e in the regulating planetary gear mechanism is fixed to the crankcase, and includes a planetary gear having a pitch circle diameter of 2e. The rotation eccentric disk with an eccentricity e is arranged coaxially with the center of the planetary gear so that it can rotate with the crank pin on the crankshaft, and the rotation eccentric disk is combined with the piston unit in a straight line by being rotatably combined with the lower end of the piston rod. In an engine that reciprocates at a stroke 4e,  The engine is a unit engine with a combination of two cylinders arranged horizontally facing each other, and a unit component engine consisting of two unit unit engines connected in series to form four cylinders opposed horizontally. One or a plurality of components are connected to each other, and the pistons facing each unit engine are configured to share a mouth end.  Furthermore, the cycloidal reciprocating engine is characterized in that the phase angle of the crank angle of the unit engine in the unit component engine is 180 °. 2. The unit component engine according to claim 1, wherein the unit component engine is configured to transmit power to other members at an integral structure portion of a crankshaft located in the middle of the unit unit engines. Cycloid reciprocating engine. [3] The cycloid reciprocating engine according to claim 1 or 2, wherein the piston has a flat shape in which a piston head has a short crankshaft direction. [4] Tolerance of linear motion error that corresponds to and allows linear motion error of the piston unit between any two elements of the piston unit, rotation eccentric disk, and cylinder, or all elements The cycloid reciprocating engine according to claim 1, 2 or 3, further comprising a structure. 5. The cycloidal reciprocating engine according to claim 4, wherein the linear motion error allowing structure is configured by sufficiently taking a piston unit and a cylinder clearance. [6] The linear motion error allowing structure is configured such that the rotating eccentric disk of the restriction planetary gear mechanism is attached to a rod end via a movable block having a slight operating clearance in a direction perpendicular to the cylinder sliding direction. The cycloidal reciprocating engine according to claim 4, wherein  7. The linear motion error permissible structure is characterized in that the piston unit rod end is divided into two, and the piston unit as a whole is configured to be slightly refractable with the rod end as a boundary. Cycloid reciprocating engine. 8. The cycloid reciprocating engine according to claim 1, 2, 3, 4, 5 or 6, wherein each opposed piston in the unit unit engine is integrally formed as an opposed piston.  [9] The cycloid reciprocating engine according to claim 1, 2, 3, 4, 5, 6, 7 or 8, wherein a crank web of the cycloidal reciprocating engine is supported by a crankcase on a circumferential surface thereof. Reanimation agency.  [10] When the unit component engines are combined with N (N = 1, 2, 3, ···) groups to form a horizontally opposed 4N cylinder, the connecting parts of the crankshaft between the unit component engines are 10. The component according to claim 1, 2, 3, 4, 5, 6, 7, 8 or 9, wherein the phase difference of the crankshaft is set to a predetermined value (180 ° / N) at the connecting portion of the unit component engine. Cycloid reciprocating engine.  [11] The transmission shaft of the cycloid reciprocating engine is one obtained by integrally connecting those taken out from each unit component engine, 1, 2, 3, 4, 5, 6, Cycloid reciprocating engine according to 7, 8, 9 or 10.  [12] The imbalance between the reciprocating mass inertial force and the inertial torque in the case of the horizontally opposed four-cylinder configuration shown by N = 1 described above leaves only the crank torque due to the reciprocating mass inertia as an unbalancer. 3. The structure according to any one of claims 1 and 2, characterized in that it is configured so as to be balanced dynamically by smoothing a crank torque generated by an expansion force generated in a working chamber defined by a piston and a cylinder. 3, 4, 5, 6, 7, 8 or 9 cycloid reciprocating engine. [13] The reciprocating mass of the horizontally opposed 8-cylinder configuration shown by N = 2 The unbalance of inertial force and inertial torque is based on the fact that each crankshaft is placed at a predetermined phase angle difference (180 ° / N, N = 2) when connecting the unit component engines. End balancers are provided at both ends of the crankshaft, and the counterbalancer of the transmission shaft that transmits power to the outside at the center of the crankshaft located in the center of each unit engine is configured to balance kinetically. The cycloid reciprocating engine according to claim 1, 2, 3, 4, 5, 6, 7, 8, 9, 10 or 11. [14] In the case of a cylinder configuration having 12 or more horizontally opposed cylinders represented by N≥3, the unbalance between the reciprocating mass inertial force and the inertial torque is caused by 3. The structure according to claim 1, wherein the shafts are arranged at a predetermined phase angle difference (180 ° / N, N = 3, 4,...) So as to be balanced dynamically. 3, 4, 5, 6, 7, 8, 9, 10 or 11 cycloid reciprocating engine.  [15] The cycloid according to claim 1, 2, 3, 4, 5, 6, 7, 8, 9, 10, 11, 12, 13 or 14, wherein the engine is a four-cycle engine. Reciprocating engine.  [16] The cycloid according to claim 1, 2, 3, 4, 5, 6, 7, 8, 9, 10, 11, 12, 13 or 14, wherein the engine is a two-cycle engine. Reciprocating engine.  [17] The crank mechanism used in the cycloidal reciprocating engine according to claim 1, 2, 3, 4, 5, 6, 7, 8, 9, 10, 11, 12, 13 or 14. A pump device characterized by being used.