JPH03352A - Reciprocating transmission device - Google Patents

Abstract

PURPOSE: To achieve complete balance as a rotating body by preventing relative rotations of a rotary pin which movably stores a reciprocating pin at the fixed part of a driveshaft and a pinion, causing a crank arm adjacent to an auxiliary transmission device to project into an internal gear, and providing a balancer for the pinion and a reciprocating pin. CONSTITUTION: A rotary pin 7 is rotatably placed via a support shell 6 in an annular member 5 provided at the connecting rod 4 of a piston 3, and a pinion 8 meshing with an internal gear 9 provided at a flange bush 10 secured to a casing 21 is coupled to the rotary pin 7 in such a way as to be non-rotatable relative thereto and eccentric therewith, to form a Cardan circle pair type auxiliary transmission device 11. A reciprocating pin 13 having a crankshaft 12 is supported in such a way as to be rotatable and slidable against the pinion 8 and is secured to the crankshaft 14 projected into the internal gear 9 within each end area and is provided with a balancer 15. Therefore, the rotary pin 7 is formed as a rotating body with respect to a rotation axis and can be held completely balanced.

Description

DETAILED DESCRIPTION OF THE INVENTION [Industrial Application] The present invention comprises a rotating pin supported in a connecting rod and an auxiliary transmission for rotating the rotating pin in a direction opposite to the drive shaft of an engine. the rotating pin includes an eccentrically disposed reciprocating pin for driving connection with the drive shaft; the auxiliary transmission includes a pinion disposed coaxially with the reciprocating pin and meshing with the internal gear; the radius of the pinion is It concerns a reciprocating transmission, in particular a reciprocating piston engine, in which the connecting rod is guided in a straight line by determining the eccentricity of the reciprocating pin and choosing it to be half the radius of the ring gear.

[Conventional technology and problems]

The kinematic basis of this type of reciprocating transmission is formed by an auxiliary transmission having a Cardan circle pair. In a Cardan pair, a small gear rolls inside a large gear without slipping. When the diameter of the internal gear is twice the diameter of the small gear, that is, the pinion, the two diametrically opposed dots of the pinion, when rolling inside the internal gear,
A diagonal linear reciprocating motion and a purely sinusoidal reciprocating motion are performed. An engine part 1 connected to one of the two points, for example, a connecting rod of a reciprocating piston engine,
Perform a linear reciprocating motion. The connection between one connecting rod and the pinion at the same point consists of two eccentrics controlled in opposite directions and one
This can be done in combination with two driven shafts or by a crank or crankshaft with an eccentric. In the latter case, the eccentric also rotates in a direction opposite to the direction of rotation of the crankshaft when the externally toothed pinion is guided in the internal gear.

1 with a connecting rod and a driven shaft used in a single cylinder reciprocating piston engine or a double cylinder reciprocating piston engine
Compensation of the rotating and vibrating inertia of a reciprocating transmission by how one or more eccentrics, the crankshaft, and an auxiliary transmission, also known as an endocycloid transmission, are interrelated. Various solutions are available for the arrangement of the balancers required to do this.

For example, in the endocycloid reciprocating transmission disclosed in West German Patent No. 2720284, the turbidity of the pinion that causes the reciprocating movement of the connecting rod with the piston is as follows:
It is considered the first center of weight. At this center of weight,
An opposing weight section is attached on another dot that reciprocates at right angles to this. These two centers of mass on the axis of the pinion are considered one. Attached to this weight center, which is considered as one, are diagonally opposite opposing weight portions that form a circle around the center of the internal gear. Thus, an auxiliary transmission is obtained which is statically and dynamically balanced with respect to the weight part reciprocating through one revolution around the axis of the internal gear, i.e. around the coaxial axis of the driven shaft. In order to achieve this weight balance, this known reciprocating transmission has a first eccentric body which is connected in a rotationally fixed manner to the driven shaft. A second eccentric, which is connected to the connecting rod, is attached to the first eccentric so as to be movable in the opposite direction to the first eccentric via an auxiliary transmission. In this case, in order to obtain an equilibrium state of the weight part, the rotational movement of the center of the first eccentric around the drive shaft causes the rotational movement of the center of the second eccentric around the center of the first eccentric. It is assumed that the movement of the center of the second eccentric body is obtained by overlapping the rotational movement. An additional weight section is added to this reciprocating weight section. This additional weight portion sets the center of gravity of the vibration system at the center of the second eccentric body. Thus, by means of the first additional opposing weight part provided on the second eccentric, the center of gravity of said weight part is set at the center of the first eccentric. Due to the second counterweight part provided on the first eccentric, the center of gravity of the entire system is set at the geometrical axis of the main shaft or internal gear, thereby achieving perfect static and dynamic equilibrium. A reciprocating transmission device is obtained.

As the embodiment illustrated in the drawing of DE 27 20 284 shows, the counterweights used to achieve the dynamic balance are a pair of counterweights arranged approximately symmetrically in the plane of the connecting rod. It is divided into. This results in a reciprocating transmission that is relatively wide and complex in construction. A further disadvantage of this reciprocating transmission is that the additional weight section increases not only the vibrating weight section but also the first and second opposing weight sections, thus resulting in a relatively heavy reciprocating transmission.

In order to eliminate the above-mentioned drawbacks of this known reciprocating transmission,
A reciprocating transmission was proposed in DE 32 32 100 A1. In this reciprocating transmission, no additional weight is provided for the vibrating weight of the piston and connecting rod.

By reducing weight by eliminating additional weight,
The diameters of the first and second opposing weight parts can also be reduced. In this case, the center of gravity of the vibrating weight part is shifted to the center of the second eccentric body. However, this reciprocating transmission also has a first and a second eccentric body and the opposing weights are arranged in pairs and symmetrically with respect to the plane of the connecting rod, so that it is particularly suitable for a transmission for reciprocating piston engines. When applied, it results in a similarly wide configuration. A common drawback of the two reciprocating transmissions mentioned above is the relatively complex construction of the auxiliary transmission.

In the reciprocating transmission for a reciprocating piston engine known from Swiss Patent No. 480,567, the connecting rod of the piston engages in a reciprocating pin of the crankshaft.

The crankshaft is rotatably supported within a disc that is rotatably supported in the outer circumferential direction within the engine casing by a main pin provided in an eccentrically arranged through hole. In this case, an auxiliary transmission is used to rotate the crankshaft in the opposite direction to the disc. In order to obtain perfect weight balance, a counterweight is arranged on the side of the reciprocating pin of the crankshaft, and another counterweight is arranged on the disk. This configuration also increases the width of the reciprocating transmission and complicates the configuration of the auxiliary transmission.

The reciprocating transmission known from DE 22 41 973 has a narrow design in the width direction of the engine (this reciprocating transmission forms the basis of the present invention). This reciprocating transmission device has a rotating pin in which a reciprocating pin is eccentrically arranged at the center of gravity of a double piston for an opposed reciprocating piston internal combustion engine. Furthermore, an internal gear is arranged coaxially with the 5-rotation pin in the double piston. The drive shaft arranged transversely to the double piston is divided into two parts, each part of the drive shaft being used to receive a reciprocating pin via a blind hole arranged on the end side.

Further, a pinion is disposed coaxially with the blind hole in a concave portion on the end surface side of one drive shaft portion so as to be relatively non-rotatable. The pinion meshes with an internal gear that is arranged non-rotatably on the multiple pistons.

A disadvantage of this known reciprocating transmission is that the drive shaft is divided into two parts. The manufacture of each drive shaft section is complicated in order to precisely position the eccentric blind hole in terms of eccentricity and parallelism of the drive shaft section to the axis of rotation. It is also manufactured that each drive shaft section must be supported with a relatively small support gap in the direction of its outer periphery in order to achieve a non-tightening cooperative action of the reciprocating pin that engages the blind hole with a support gap. It's a hassle. Furthermore, in order to prevent the auxiliary transmission from tilting movement via the drive shaft section,
A relatively wide running surface must be provided on the outer periphery of the engine casing for each drive shaft section, which disadvantageously results in a wide engine casing construction. Overall, this known reciprocating transmission does not provide smooth movement.

[Problem to be solved by the invention]

The object of the invention is to provide a reciprocating transmission of this type with a drive shaft which is integral during installation, the construction of which drives perfectly balancing the weight of the rotating parts of the reciprocating transmission. It is an object of the present invention to provide a reciprocating transmission device which is advantageous in the following.

[Means to solve the problem]

In order to solve the above-mentioned problems, the present invention provides that an internal gear is fixed to a casing, a pinion is coupled to a rotating pin in a relatively non-rotatable manner, and a reciprocating pin is movably arranged within the rotating pin, and is used as a crankshaft. The crank arm, which is a fixed part of the formed drive shaft and is adjacent to the auxiliary transmission, protrudes endward into the internal gear. It is characterized in that it is provided with a balance body for the pinion and the reciprocating pin, and that the rotating pin is perfectly balanced as a rotating body with respect to its axis of rotation.

The invention has several steps. An important step is to arrange the pinion on the end face of the rotating pin so that it cannot rotate relative to it. This allows the reciprocating pin to be slidably arranged within the rotary pin instead of being coupled in a relatively rotationally immovable manner to the eccentric reciprocating pin. In a further step, the reciprocating pin is configured as part of a drive shaft formed as a crankshaft.

In this case, the reciprocating pin is fixed at least to the crank arm of the crankshaft. If this crank arm is also designed to be adjacent to an auxiliary transmission with an internal gear which is fixed to the casing, another step is to carry out the following steps: on the one hand, by means of the internal gear and the pinion, and, on the other hand, in the axial direction by the rotating pin and the crank. The free space defined by the arm is used to locate the counterbalance for the pinion and reciprocating pin on the crank arm. This results in a compact reciprocating transmission. In order to further balance the rotating weight of the reciprocating transmission, it is advantageous for the reciprocating pin to be movably arranged on the rotating pin. This means that a single rotation pin acts as a rotating body (rotatorisch) about its axis of rotation.
This is because it is possible to maintain perfect equilibrium. A further important advantage of the present invention is that the internal balance of one part by weight is limited to the rotating part of the reciprocating transmission. In the reciprocating transmission according to the invention, it is therefore possible to eliminate the respective weight balance for the rotating and vibrating weight parts.

In a rotating counterbalanced weight part, there is no need to provide an additional weight part for the vibrating weight part in order to set the overall center of gravity at a suitable position within the reciprocating transmission, as is the case in the prior art. As a result of the reduced mechanical load, the moment of inertia of the reciprocating transmission is therefore reduced. Therefore, it is advantageous that the reciprocating transmission device can be constructed compactly.

In order to balance the oscillating inertial forces imparted by the connecting rod of the piston in a reciprocating piston machine and by the rotating pin reciprocating with the connecting rod, according to embodiment item 1, the Two countershafts equally spaced on either side of the shaft are provided with counterbalances aligned with respect to the plane of the connecting rod. This balance body is out of phase with respect to the oscillating body, so that the countershaft carrying the balance body rotates at the speed of the crankshaft. Envelope type transmission (Hii
According to Embodiment 5, for an opposed four-stroke reciprocating piston internal combustion engine, the turning gear required for envelope transmission in the plane is Used for driving the control axis. This advantageously simplifies the configuration for driving the subshaft and the control shaft.

According to embodiment items 2 and 3, each reciprocating transmission includes two
A crankshaft with two crank arms is provided. One crank arm is located immediately adjacent to the rotating pin and the other crank arm is located immediately adjacent to the auxiliary transmission.

In order to shorten the support length, the two crank arms are each supported on the outer periphery of the housing via sliding surfaces.

Furthermore, if the diameter of the crank arm disposed immediately adjacent to the rotating pin is made smaller than the diameter of the rotating pin, the rotating pin attached to the reciprocating pin and the pinion fixed thereto are both connected to the crankshaft in the connecting rod that confines the rotating pin. can be installed from one side.

The configuration described in embodiment item 4 makes it more advantageous to attach the crankshaft from one side of the crankshaft supported in the outer circumferential direction of the disc-shaped crank arm. That is, the crank arm adjacent to the auxiliary transmission is supported in a flange bushing arranged centrally in the housing, which flange bushing carries the internal toothing of the internal gear on the side of the rotary pin. This allows the manufacturing tolerance to be reduced by tJs.

By selecting and using the teeth of the auxiliary transmission according to embodiment item 9, the diameters of the internal gear and pinion of the auxiliary transmission can be made relatively small. As a result, the distance between the reciprocating pin and the axis of rotation of the crankshaft can be made favorable, that is, the eccentricity of the reciprocating pin with respect to the axis of rotation of the rotary pin can be made favorable. The outer diameter of the rotary pin, which is slidably supported in the connecting rod, can thus be selected to be relatively small. In an endocycloid type reciprocating transmission with a radius ratio of 2 = 1, the stroke between top dead center and bottom dead center is equivalent to four times the eccentricity mentioned above, so the diameter of the rotating pin is shortened. , and with the arrangement according to embodiment 7, the diameter of the adjoining cylinder can be selected to be larger than the diameter of the rotary pin, so that the rotary pin can be accommodated in the connecting rod or provided for this purpose. The annular member may be in a closed configuration. Such a closed configuration allows the diameters of the cylinder and the annular member or rotating pin to be matched to each other so that the annular member of the connecting rod can be inserted into the sill, resulting in an axially compact reciprocating transmission, i.e. Not only can the engine be obtained, but the size of the engine is also shorter in width or height.

Furthermore, when the reciprocating transmission according to the invention is configured according to embodiment 7, the advantage is obtained that the connecting rod can be constructed lightweight and robust due to the compact and robust construction and the above-mentioned division of weight.

In this case, the part of the connecting rod between the annular element for the rotary pin and the piston, which is integrally connected to the connecting rod, is rod-shaped. This allows for a considerable reduction in the number of vibrating bodies and provides manufacturing advantages over multiple pistons in opposed reciprocating piston engines.

Furthermore, multiple pistons can be arranged through the opening of one cylinder. In this case, in the central position of the cylinder, the reciprocating transmission device according to the invention is installed, with the weight of the rotating parts internally balanced, and at one angle transversely to the rotating parts.
Mounting times can be arranged in process.

〔Example〕

Next, embodiments of the present invention will be described using the accompanying drawings.

The opposed reciprocating piston engine 1 has cylinders 2 arranged in alignment with one another. A piston 3, which is arranged to reciprocate within the cylinder 2, is mounted on a common connecting rod 4. The connecting rod 4, which is integrally connected to the two pistons 3, has a closed annular member 5 in its central part.
have. A rotary pin 7 is rotatably arranged within the annular member 5 via a support shell 6 . Rotating pin 7
A pinion 8, which is eccentrically arranged, is connected to the pinion 8 so as to be non-rotatable. The pinion 8 has its radius R1 (amount e)
It is provided on the rotating pin 7 so as to be eccentric by the amount. The pinion 8 has a flange bushing 10 fixed to the casing.
It meshes with the inner car 9 installed in the. The radius of the internal gear 9 is R2, which is twice the radius R of the pinion 8. The internal gear 9 and the pinion 8 thus form an auxiliary transmission 11 of the Cardan pair type.

The reciprocating piston engine 1 has a crankshaft 12 equipped with a reciprocating pin 13 as a drive shaft. The reciprocating pin 13 is disposed coaxially with the pinion 8, and is slidably supported by the rotating pin 7 and the pinion 8, which is connected to the kneader in a relatively non-rotatable manner. Further, the reciprocating pin 13 is fixed to the crank arm 14 of the crankshaft 12 at both end regions thereof.

The crank arm 14 is formed into a disk shape and is supported so as to be slidable in the outer diameter direction. The crank arm 14 adjacent to the auxiliary transmission 11 has a counterbalance 1 for the pinion 8 and the reciprocating pin 13 which projects into the internal gear 9 on its end side.
It is equipped with 5. As can be seen from FIG. 2, the rotating pin 7 maintains perfect balance as a rotating body with respect to its rotational axis due to the recessed portion. The reciprocating transmission for the reciprocating piston engine 1, consisting of the crankshaft 12, the auxiliary transmission 11 and the rotating pin 7, is therefore perfectly balanced as a rotating body.

In order to compensate for the oscillating inertia of the piston 3, the connecting rod 4 and the rotating pin 7 which reciprocates with the connecting rod 4, a counterbalance 17 provided on the countershaft 16 is used (FIG. 2). The two countershafts 16 extend parallel to each other at equal intervals from the crankshaft 12 on both sides of the crankshaft 12 so as to intersect the plane of the connecting rod 4 . A subshaft 16 that rotates at the rotation speed of the crankshaft 12
are provided in each case adjusted relative to the plane of the connecting rod 4.
et) carrying a compensator 17; Reciprocating piston engine 1
When the is used as a 4-stroke internal combustion engine, both shafts 1
6, an envelope transmission 18 with a deflection gear 19 is provided. In this case, the deflection gear 19 is used to drive the control shaft 20. The control shafts 20 are spaced apart from adjacent subshafts 16 at equal intervals. The other countershaft 16 can be used to drive additional equipment, such as a lighting machine, for example. In this case, the parts rotating in the opposite direction to the crankshaft 12 are used to reduce the reaction moment of the reciprocating piston engine 1.

Further, as can be seen from FIG. 2, the annular member 5 of the connecting rod 4
The outer diameter of the cylinder is selected in relation to the diameter of the rotary pin 7 in such a way that the annular member 5 of the reciprocating connecting rod 4 enters the drive-side end region of the cylinder 2 in which the piston 3 is accommodated. has been done. With such a configuration, a reciprocating piston engine 1 having two shorter widths can be obtained. In the case of the embodiment shown in FIG. 1 configured as described above, the reciprocating piston engine 1 having a short length is connected to the casing via the sliding surface on the outer periphery of the crank arm 14 formed in a disc shape and the flange bushing 10. 21
obtained by being supported within. In this case, the crankshaft 12 is supported on the one hand by means of the rotary pin 7 and on the other hand by means of the internal gear 9 of the auxiliary transmission 11. For the installation of a reciprocating transmission consisting of a crankshaft 12, an auxiliary transmission 11 and a rotating pin 7, it is advantageous if the crank arm 14 directly adjacent to the rotating pin 7 has a smaller diameter than the rotating pin 7. It is. Therefore, if the connecting rod 4 is arranged centrally, the reciprocating transmission can be mounted from one side from the drive side of the reciprocating piston engine 1 6 , i.e. because of the rotating pin 7 provided in the connecting rod 4 with the front piston arm 14 . It can be installed by positioning it through the support hole.

When the auxiliary transmission 11 is configured in a cardan pair type in order to rotate the rotating pin 7 in the opposite direction with respect to the crankshaft 12, as is well known, the stroke of the connecting rod 4 is equal to the stroke of the internal gear 9.
It is twice the radius R2 of .

If the reciprocating piston engine 1 used as an internal combustion engine has a normal diameter for the cylinder 2 and the stroke of the connecting rod 4 is short, the internal gear 9 and the pinion are used in order to reliably control the load on the auxiliary transmission 11. The tooth is selected for 8.

Within the scope of the invention, in the case of a two-samoton internal combustion engine constituted by a slot and an intake valve or an exhaust valve, the countershaft can additionally be used as a control shaft rotating in opposite directions and at the speed of the crankshaft. Can be used.

Next, embodiments of the present invention will be listed.

(1) Reciprocating piston engine (1), two subshafts (16)
is transverse to the plane of the connecting rod (14) and parallel to the crankshaft (
The connecting rod (4) is arranged parallel to the crankshaft (12) at equal intervals on both sides of the connecting rod (12), and each of the subshafts (16) that rotate at the number of rotations of the crankshaft is connected to the connecting rod (4).
carries a counterbalance (17) which is arranged eccentrically with respect to the plane of the piston (3) and the connecting rod (
4) and a rotating pin (7) that reciprocates together with the connecting rod (4).
2. The reciprocating transmission device according to claim 1, characterized in that the reciprocating transmission device adjusts the oscillating inertia force between the oscillator and the oscillator.

(2) The crankshaft (12) is directly connected to the auxiliary transmission device (11).
2. The reciprocating transmission device according to claim 1, wherein the reciprocating transmission device is supported via a crank arm (14) using a rotating pin (7) and an internal gear (9).

(3) The crankshaft (12) is supported within the casing (21) via a sliding surface on the outer periphery of a crank arm (14) formed in a disc shape, and is supported at least once by a rotating pin (
Claim 1, according to claim 1 or 2, characterized in that the crank arm (14) arranged in the immediate vicinity of the rotary pin (7) has a smaller diameter than the rotating pin (7). Reciprocating transmission.

(4) A crank arm (14) located in the immediate vicinity of the auxiliary transmission (11) is supported in a flange bush (10) centered in the casing (21), said flange bush (10) ) carries the internal gear of the internal gear (9) in its end region on the rotating pin side or on the connecting rod side. The reciprocating transmission device according to any one of the above.

(5) The countershaft (16) of the opposed four-stroke reciprocating piston engine (1) is driven via an envelope transmission (18) with a diverting gear (19), the diverting gear (19) being The reciprocating power transmission according to claim 1 or any one of the above items 1 to 4, characterized in that control shafts (2o) arranged at equal intervals are driven from the subshafts (16) of the reciprocating transmission. Device.

(6) The other subshaft (16) drives an additional device (lighting device) having a rotating body that rotates in the opposite direction to the crankshaft (12). The reciprocating transmission device according to any one of items 1 to 5.

(7) The connecting rod (4) for an opposed reciprocating piston engine has a centrally closed annular member (5);
Claim 1 or any one of claims 1 to 6 above, characterized in that the piston (3) is integrally connected to a rod-shaped part via a tapered transition part, and the piston (3) is formed integrally with this rod-shaped part. The reciprocating transmission device according to any one of the preceding paragraphs.

(8) the outer part of the annular member (5) in such a way that the annular member (5) of the vibrating connecting rod (14) enters the drive-side end region of the cylinder (2) containing the piston (3); 8. Reciprocating transmission according to claim 1 or one of the preceding claims, characterized in that the diameter is selected in relation to the diameter of the rotary pin (7).

(9) The auxiliary transmission (11) has specially selected teeth.
The reciprocating transmission device according to any one of items 8 to 8.

(10) A subshaft in a two-stroke reciprocating piston internal combustion engine constituted by a slit and an intake valve or an exhaust valve is used as a control shaft that rotates at the rotational speed of a crankshaft in opposite directions. The reciprocating transmission device according to any one of the above items 1 to 4.

[Brief explanation of drawings]

FIG. 1 is a sectional view of a reciprocating piston engine equipped with a reciprocating transmission according to the invention, and FIG. 2 is a partial end view of the reciprocating piston engine with a countershaft for adjusting the oscillating inertia force. 1... Reciprocating piston engine 4... Connecting rod 7... Rotating pin 8... Pinion 9... Internal gear 11... Auxiliary transmission device 12... Crankshaft 13... Reciprocating pin 14...Crank arm 15/balance body

Claims (1)

[Claims] (1) Rotating pin (7) supported in connecting rod (4)
and an auxiliary transmission device (11) for rotating the rotary pin (7) in a direction opposite to the drive shaft (12) of the engine (1), the rotary pin (7) being connected to the drive shaft (12). the auxiliary transmission (11) comprises a pinion (8) arranged coaxially with the reciprocating pin (13) and meshing with the internal gear (9); , the radius (R_1) of said pinion (8) determines the eccentricity (e) of the reciprocating pin (13) and is selected to be half the radius of the internal gear (9), thereby making the connecting rod (4) In the reciprocating transmission device in which the internal gear (9) is linearly guided, the internal gear (9) is fixed to the casing, the pinion (8) is coupled to the rotating pin (7) in a relatively non-rotatable manner, and the reciprocating pin (13) is a fixed part of the drive shaft arranged movably in the rotating pin (7) and formed as a crankshaft (12), and the crank arm (14) adjacent to the auxiliary transmission (11)
) is provided on its end side with a counterbalance (15) for the pinion (8) and the reciprocating pin (13), which projects into the internal gear (9), the rotary pin (7) having its axis of rotation A reciprocating transmission device characterized in that it maintains perfect balance as a rotating body with respect to.