US3693464A

US3693464A - Reciprocating-rotary motion conversion device

Info

Publication number: US3693464A
Application number: US160663A
Authority: US
Inventors: Gerhard Wieckmann
Original assignee: Individual
Current assignee: Individual
Priority date: 1971-07-08
Filing date: 1971-07-08
Publication date: 1972-09-26
Anticipated expiration: 1989-09-26

Abstract

A reciprocating-rotary motion conversion unit that is particularly adapted for use with a conventional cylinder, piston and wrist pin to more efficiently utilize the power generated when charges of fuel are intermittently exploded in timed sequence within the cylinder. The increased efficiency is attained by a unique connecting rod and gear assembly that are so operatively associated with the wrist pin and a drive shaft that the latter is rotated more than one revolution for each reciprocating cycle of the piston. In addition, the gear assembly is of such design that it has a throw that is twice the stroke of the piston, and as a result the torque exerted on the drive shaft is increased. The invention is highly advantageous from an ecology standpoint in an automotive application as a simple reciprocating cycle of the piston results in the drive shaft being rotated more than one revolution rather than one revolution as occurs in a conventional internal combustion engine. Also, due to the increased number of revolutions of the drive shaft for each cycle of reciprocation of the piston, less fuel is burned by a vehicle over that consumed in a conventional internal combustion engine, in rotating the drive shaft the same number of revolutions, and accordingly less products of combustion are discharged to the ambient atmosphere. The present invention while most adaptable to automotive combustion engines may also be used advantageously for a high speed motor to rotate the drive shaft and impart relatively low speed reciprocating movement to a piston, such as is required in pumps and the like.

Description

United States Patent Wieckmann 51 Sept. 26, 1972 [54] RECIPROCATING-ROTARY MOTION CONVERSION DEVICE [72] Inventor: Gerhard Wieckmann, 20311 Gresham St., Canoga Park, Calif. 91306 [22] Filed: July 8,1971

[21] App1.No.: 160,663

[52] U.S.Cl. ..74/52,123/l97 AC [51] Int.Cl. ..Fl6h 37/12 [58] Field of Search ..74/52; 123/197 AC, 197 R [56] References Cited UNITED STATES PATENTS 1,191,827 7/1916 Reese ..123/197 AC 1,326,129 12/1919 Chadbourne ..74/52 1,863,667 6/1932 Miranda ..74/52 1,977,075 10/1934 Magnuson....; ..123/197R 2,199,625 5/1940 Fern-brugg ..74/52 Primary Examiner-William F. ODea Assistant Examiner-Wesley S. Ratliff, .lr. Attorney-William C. Babcock 5 7 ABSTRACT A reciprocating-rotary motionconversion unit that is particularly adapted for use with a conventional cylinder, piston and wrist pin to more efficiently utilize the power generated when charges of fuel are intermittently exploded in timed sequence within the cylinder.

' assembly is of such design that it has a throw that is twice the stroke of the piston, and as a result the torque exerted on the drive shaft is increased.

The invention is highly advantageous from an ecology standpoint in an automotive application as a simple reciprocating cycle of the piston results in the drive shaft being rotated more than one revolution rather than one revolution as occurs in a conventional internal combustion engine. Also, due to the increased number of revolutions of the drive shaft for each cycle of reciprocation of the piston, less fuel is burned by a vehicle over that consumed in a conventional internal combustion engine, in rotating the drive shaft the same number of revolutions, and accordingly less products of combustion are discharged to the ambient atmosphere.

The present invention while most adaptable to automotive combustion engines may also be used advantageously for a high speed motor to rotate the drive shaft and impart relatively low speed reciprocating movement to a piston, such as is required in pumps and the like.

6 Claims, 7 Drawing Figures PATENTEDSEP26 m2 SHEET 2 [IF 3 W rk I yjiw g 4 RECIPROCA'IING-ROTARY MOTION CONVERSION DEVICE BACKGROUND OF THE INVENTION 1. Field of the Invention A reciprocating-rotary motion conversion device.

Description of the Prior Art 2. In the conventional internal combustion engine each full reciprocating cycle of a piston results in a crankshaft operatively associated therewith rotating but one revolution. Also in the conventional reciprocating invention the stroke of the piston is the same as the throw of the crankshaft. As a result, unless the stroke of the piston is relatively great, the force exerted by the piston on the moment arm of the crankshaft at the time of the initial explosion of the fuel charge is relatively small, and maximum torque on the crankshaft is not attained.

In the present invention the operational disadvantages of the prior art internal combustion engines in this regard is overcome, in that the throw of the connecting rod gear assembly is twice the stroke of the piston, and as a result maximum torque is attained from the exploding charges. In addition, each reciprocating cycle of the piston when the present invention is employed results in the drive shaft being rotated a number of revolutions, rather than one revolution as occurs in a conventional engine.

The present invention provides the further operational advantage when it is used in an automotive vehicle, that greater mileage is attained from the vehicle, and as a result contamination of the ambient atmosphere from products of combustion is lowered due to the use of less fuel per mile.

The present invention also provides the operational advantage that a high speed motor can be used in conjunction therewith, with the invention converting high speed rotary motion to relatively low speed reciprocating motion on a piston or the like.

SUMMARY OF THE INVENTION A reciprocating rotary motion conversion device particularly adapted for use with the cylinder and piston having timed ignition means associated therewith, to obtain increased torque on the drive shaft, as well as additional rotational movement of the drive shaft for each reciprocating cycle of the piston. The connecting rod-gear assembly is pivotally connected to the wrist pin of the piston in such a manner, that the throw of the assembly is twice or more the stroke of the piston. This arrangement permits the force of the exploding charge in the cylinder to be transferred to the drive shaft to increase the torque thereon, and obtain maximum power from the fuel, as well as increased efficiency in the operating characteristics of the engine.

A major object of the present invention is to provide a reciprocating-rotary motion conversion device for use with a piston in such a manner that the throw on the crankshaft is twice or more the stroke of the piston, and as a result improving the torque characteristics of an engine with which it is associated, as well as causing the drive shaft to rotate a number of revolutions for each reciprocating cycle of the piston rather than the single revolution attained in a conventional internal combustion engine.

Another object of the invention is to permit either reciprocating motion to be transformed to rotary motion or rotary motion to reciprocating motion by a relatively simply mechanical device, and one that permits these conversions to be carried out with a high degree of efficiency, and within a relatively small space.

DESCRIPTION OF THE DRAWINGS FIG. 1 is a transverse cross sectional view of an internal combustion engine embodying the invention, and with the piston disposed at substantially the top of its stroke;

FIG. 2 is the same transverse cross sectional view as shown in FIG. 1, but with the piston being at substantially the lowermost position of its stroke;

FIG. 3 is a cross sectional view of a first form of the invention taken on the line 3-3 of FIG. 1;

FIG. 4 is a cross sectional view of a second form of the invention;

FIG. 5 is a transverse cross sectional view of a third form of the invention;

FIG. .6 is a cross sectional view of the third form of the device taken on the line 6-6 of FIG. 5; and

FIG. 7 is a cross sectional view of the third form of the device taken on the line 77 of FIG. 5.

DESCRIPTION OF THE PREFERRED EMBODIMENTS and 3 that is operatively associated with a conventional cylinder defining member B that has a conventional piston C slidably mounted within the confines thereof.

The upper end of the cylinder defining member B is closed by a conventional head D that serves to removably support a spark plug E or other suitable ignition means, as well as a fuel inlet valve F and discharge valve G.

The cylinder defining member B terminates on the lower end thereof in flanges 10 that are secured by bolts 12 or other suitable fastening means to a crankcase H. The flanges 12 are in abutting contact with side pieces 14 and 16 that partially define the crankcase H, with the first side piece 14 having an end piece 18 extending therefrom that interlocks with a ribbed portion 20 of the second side piece 16 and is removably secured thereto by bolts 22 or other suitable fastening means.

The first side piece 14 has an opening 14a formed therein that is engaged by a cylindrical boss 24 that forms a part of a hollow rigid body 26. The interior surface of the boss 24 rigidly supports the outer race 28 of a ball bearing assembly J. The assembly J includes an inner race 30, and a sequence of balls 32 situated between the inner and outer races.

Second; side wall 16 includes an outwardly cupshaped portion 34 that has a bore 34a formed therein that is axially aligned with a counterbore 34b also defined in the portion 34. The bore 340 and counterbore 34b are at their junction separated by an inwardly extending circular rib 34c. The bore 34a serves to support a ball bearing assembly K that includes an outer race 36 and inner race 38 and a sequence of balls 40 situated therebetween. The counterbore 34b supports a ball bearing assembly L that has an outer race 42 that is seated in abutting contact with the bore 34a. Assembly L includes an inner race 44 and a sequence of balls 46 situated between the two

races

42 and 44.

The piston C is provided with a wrist pin 48 as is conventional with such devices, with the pin being pivotally connected to a connecting rod M that develops on its lower end into a relatively large ringshaped portion 50 that rigidly supports an internal gear 52 within the confines thereof.

Two generally semi-circular first and

second counterweights

54 and 56 are provided that have gear carrier portions 54a and 56a extending outwardly therefrom and normally disposed thereto as best seen in FIG. 1. Counterweight 54a has a shaft 58 formed integral therewith as shown in FIG. 3 that extends outwardly therefrom. Shaft 58 is in engagement with the inner race 30 of ball bearing assembly J. The shaft 58 has a gear 60 rigidly secured thereto, that is in toothed engagement with a gear assembly 62 of conventional design, which gear assembly as it rotates is adapted to cause the sequential firing of the spark plug E, as well as causing the sequential opening of the valves F and G as is conventional with an internal combustion engine.

The counterweight portion 56a as shown in FIG. 3 has a number of bores 56b formed therein that are axially aligned with tapped bores 54b formed in the counterweight portion 54a. Screws 64 extend through the bores 56b and rigid tubular spacers 66 to engage the tapped bores 54b. The screws 64 when tightened force the counterweight portions 54a and 560 into pressure abutting contact with the ends of the spacers 66 to provide a space 68 of predetermined width between the

counterweights

54 and 56 as well as the portions 54a and 56a.

Three equally spaced openings 56c are formed in the counterweight portion 56a and are axially aligned with tapped bores 54c formed in the counterweight portion 55a. The three openings 56c have screws 68 extending therethrough that rotatably support

planetary gears

70a, 70b and 70c when the threaded portion of the screws are in engagement with the tapped bores 54c. The

gears

70a, 70b and 700 as may best be seen in FIG. 1 are in toothed engagement with the internal gear 52.

Counterweight 56 as shown in FIG. 3 has a hollow tubular shaft 72 extending outwardly therefrom that has the exterior surface thereof in abutting contact with the interior surface of the inner race 36 and being rotatably supported relative to the crankcase H as a result thereof. The shaft 72 has a longitudinally extending bore 74 formed therein with the bore 74 on its inner end supporting a conventional ball bearing assembly 76. A recess 78 formed in the first counterweight 54 also serves to support a ball bearing assembly 80 that is identical to the ball bearing assembly 76.

The inner race 44 of ball bearing assembly L rotatably supports a drive shaft N that develops on its left hand end into a section 82 of smaller diameter, and this section in turn on its left hand end developing into a second section 84 of still smaller diameter. The second section 84 is by a key 86 rigidly secured to a drive gear 88, which drive gear is in toothed engagement with the internal gear 52. The second drive shaft section 84 as can best be seen in FIG. 3 is rotatably supported by the inner races of the ball bearing assemblies 76 and 78.

When the piston C is at the top of the stroke as shown in FIG. 1, the gear a is vertically and axially aligned with the center of the drive gear 88. The distance 8 between the center of the gear 70a and the gear 88 determines the stroke of the piston C. In FIG. 1 it will be seen that the center of the gear 70a is a distance S above the center of the gear 88. The gear 88 rotates in a stationary position relative to the crankcase H as shown in FIG. 3.

When the piston C has moved downwardly to the bottom of the stroke as shown in FIG. 2, the gear 70a is now axially and vertically aligned with the gear 88, but is situated the distance S therebelow. Thus, the throw of the counterweight carrier portions 54a and 560 with the gears operatively associated therewith is 2S, which is twice the stroke of the piston C, in contrast to the stroke and throw being the same as occurs in a conventional internal combustion engine in which a conventional piston, connecting rod and crankshaft are used.

The distance S provides an increased lever arm for the force exerted by the exploding charge of fuel (not shown) in the cylinder B to act on, and accordingly the energy of the exploding charge exerts a greater torque on the drive shaft N as well as rotating the drive shaft more than one revolution for each complete reciprocating cycle of the piston C. The number of revolutions that the drive shaft N will rotate for each complete reciprocating cycle of the piston C is determined by:

(pitch diameter internal gear 52)/( pitch diameter drive gear-88) l number of rotations of drive shaft N for each complete reciprocating cycle of piston C A second form of the invention A is shown in FIG. 4 that is identical with the first form, other than that the drive shaft N merely has one section 82' extending therefrom which by a key 90 is secured to the shaft 58'. The shaft 58' is not connected to the counterweight 54' as in the first form of the invention, and as a result the shaft N and shaft 58' rotate at the same speed and in the same direction. The shaft 58 in the first form of the invention rotates one revolution for each complete reciprocating cycle of the piston C. The cup-shaped portion 34 is eliminated in the second side piece 16 in the second form of the invention A and the shaft N A being rotatably supported by two ball bearing assemblies K and L' that are of the same size and removably held in a fixed position relative to the second side piece 16' by a removably ring-shaped plate 92 that is secured thereto by screws 94 or other suitable fastening means. Elements in the second form A of the invention that are common to the first form A are designated on the drawings by the same numbers and letters but with a prime being added thereto.

A third form A" of the invention is shown in FIGS. 5, 6, and 7 that is similar in structure to the first form A.

Elements of the third form A" that are common to the first form A are designated on the drawing by the same numbers and letters as used in the first form but with double primes being added thereto.

The third form A" differs primarily from the first form A in that the drive gear 88" is not in toothed engagement with the internal gear 52" as is clearly shown in FIG. 5, and with the drive gear being secured by conventional means 96. A drive gear 88 is in toothed engagement with planetary gear 70a" and this latter gear also being in engagement with the internal gear 52 The planetary gear 700" is illustrated in FIG. 5 as being of substantially larger diameter than the planetary gears 70b" and 70c". The counterweight gear carrier portions 54a" and 56a" have recesses formed therein in 1 which identical ball bearing assemblies U and V are disposed that rotatably engage the shaft Q.

The distance S" between the center of rotation of the planetary gear 70a" and the center of the gear 88" determines the throw of the piston C". The throw of the carrier portions 54a" and 56a" with the associated gears is 28'. The number of rotations that the shaft Q will make for each complete reciprocating cycle of the piston C" is determined by the followings:

(Pitch diameter internal gear 52b")! (Pitch diameter drive gear 88")+ 1 =Number of rotations of drive shaft 0 for each complete reciprocating cycle of piston C" The use and operation of the three forms of the invention have previously been described in detail and further description is accordingly not required.

The invention has been illustrated as being applied to an internal combustion engine, but it will be obvious that if a motor (not shown) is caused to drive the shaft N, N or Q, and appropriate fluid inlet and outlets are provided in conjunction with the cylinder defining member B, B or B", that a high speed motor may be used to impart relatively slow reciprocating movement to the piston for pumping purposes or the like.

Iclaim:

1. In combination with a cylinder defining member, a piston slidably supported in said cylinder, said piston including a wrist pin, a hollow case connected to said cylinder defining member, said case including first and second side pieces, a first drive shaft rotatably sup ported in said case, a device for selectively transforming reciprocating movement of said piston to rotary motion of said piston to rotary motion of said drive shaft or rotary motion of said drive shaft to reciprocating movement of said piston, said device including:

a. a connecting rod that has first and second end portions, said first end pivotally connected to said wrist pin, said end portion disposed in said case, second end said second end portion in the form of a ring that has an internal diameter substantially greater than the diameter of said drive shaft, and said shaft extending through said second end portion;

b. an internal gear rigidly secured to the interior of said second end portion;

0. a drive gear rigidly secured to said drive shaft, said drive gear situated in said case and within the confines of said internal gear and in toothed engagement with the latter;

d. two laterally spaced first and second counterweights that include outwardly extending first and second gear carrier portions that are disposed in said case on opposite sides of said second portion of said connecting rod;

e. first means that rotatably support said first and second counterweights and carrier portions in said case to revolve about the longitudinal axis of said drive shaft;

f. second means for holding said first and second counterweights and carrier portions in predetermined lateral spacing; and

g. at least one planetary gear rotatably supported between said first and second gear carrier portions and in toothed engagement with said internal gear, with the centers of rotation of said drive gear and planetary gear being coaxially aligned on the Ion gitudinal axis of said connecting rod when said piston is a maximum distance from said drive shaft, with the distance between the centers of rotation of said drive gear and planetary gear being the stroke of said piston as said drive shaft rotates, with the throw of said planetary gear being twice said stroke as said counterweights and gear carrier portions rotate about the center of rotation of said drive gear, and the number of rotations said drive shaft makes for each complete reciprocating cycle of said piston being the ratio of the internal tooth diameter of said internal gear to the tooth diameter of said drive gear minus one.

2. A device as defined in claim 1 in which said drive shaft is joumalled in a portion of said second side piece, and said first means includes:

h. a first shaft that extends outwardly from said first counterweight and a second tubular shaft that extends outwardly from said second counterweight away from said first shaft and that envelopes at least a part of said drive shaft; and

i. first and second bearings rigidly supported from said first and second side pieces that rotatably support said first and second shafts, with said first shaft rotating at a different rate of rotation than said drive shaft.

3. A device as defined in claim 1 in which said first means includes:

h. a first shaft coaxially aligned with said drive shaft;

i. key means for removably connecting said first shaft to said drive shaft, with said drive shaft and first shaft having portions thereof extending through transversely aligned openings in said counterweight; and

j. first and second bearings supported from said first and second side pieces, with said first and second bearings rotatably supporting said first shaft and said drive shaft.

4. A device as defined in claim 1 in which said drive shaft extends through transversely aligned openings in said first and second counterweights, and said first means are first and second bearings mounted on said first and second side pieces and rotatably supporting said drive shaft.

5. In combination with a cylinder defining member, a piston slidably supported in said cylinder, said piston including a wrist pin, a hollow case connected to said cylinder defining member, said case including first and second side pieces, a first drive shaft rotatably supported in said case, a device for selectively transforming reciprocating movement of said piston to rotary motion of said piston to rotary motion of said drive shaft or rotary motion of said drive shaft to reciprocating movement of said piston, said device including:

a. a connecting rod that has first and second end portions, said first end pivotally connected to said writs pin, said second end portion disposed in said case, with said second end portion in the form of a ring that has an internal diameter substantially greater than the diameter of said drive shaft, and said shaft extending through said second end portion;

b. an internal gear rigidly secured to the interior of said second end portion;

c. a drive gear rigidly secured to said drive shaft said drive gear situated in said case and within the confines of said internal gear, but not in toothed engagement with the latter;

d. two laterally spaced first and second counterweights that include outwardly extending first and second gear carrier portions that are disposed in said case on opposite sides of said second portion of said connection rod;

g. at least one planetary gear rotatably supported between said first and second gear carrier portions and in toothed engagement with said internal gear and said drive gear, with the centers of rotation of said drive gear and planetary gear being coaxially aligned on the longitudinal axis of said connecting rod when said piston is a maximum distance from said drive shaft, with the distance between the centers of rotation of said drive gear and planetary gear being the length of the stroke of said piston as said drive shaft rotates, with the throw of said planetary gear being twice said stroke as said counterweights and gear carrier portions rotate about the center of rotation of said drive gear, and the number of rotations said drive shaft makes for each complete reciprocating cycle of said piston being the ratio of the internal tooth diameter of said internal gear to the tooth diameter of said drive gear plus one.

6. A device as defined in claim 5 in which said drive gear extends through transversely aligned openings formed in said counterweights, and said first means are bearings mounted in said openings that rotatably support said drive shaft.

Claims

1. In combination with a cylinder defining member, a piston slidably supported in said cylinder, said piston including a wrist pin, a hollow case connected to said cylinder defining member, said case including first and second side pieces, a first drive shaft rotatably supported in said case, a device for selectively transforming reciprocating movement of said piston to rotary motion of said piston to rotary motion of said drive shaft or rotary motion of said drive shaft to reciprocating movement of said piston, said device including: a. a connecting rod that has first and second end portions, said first end pivotally connected to said wrist pin, said end portion disposed in said case, second end said second end portion in the form of a ring that has an internal diameter substantially greater than the diameter of said drive shaft, and said shaft extending through said second end portion; b. an internal gear rigidly secured to the interior of said second end portion; c. a drive gear rigidly secured to said drive shaft, said drive gear situated in said case and within the confines of said internal gear and in toothed engagement with the latter; d. two laterally spaced first and second counterweights that include outwardly extending first and second gear carrier portions that are disposed in said case on opposite sides of said second portion of said connecting rod; e. first means that rotatably support said first and second counterweights and carrier portions in said case to revolve about the longitudinal axis of said drive shaft; f. second means for holding said first and second counterweights and carrier portions in predetermined lateral spacing; and g. at least one planetary gear rotatably supported between said first and second gear carrier portions and in toothed engagement with said internal gear, with the centers of rotation of said drive gear and planetary gear being coaxially aligned on the longitudinal axis of said connecting rod when said piston is a maximum distance from said drive shaft, with the distance between the centers of rotation of said drive gear and planetary gear being the stroke of said piston as said drive shaft rotates, with the throw of said planetary gear being twice said stroke as said counterweights and gear carrier portions rotate about the center of rotation of said drive gear, and the number of rotations said drive shaft makes for each complete reciprocating cycle of said piston being the ratio of the internal tooth diameter of said internal gear to the tooth diameter of said drive gear minus one.

2. A device as defined in claim 1 in which said drive shaft is journalled in a portion of said second side piece, and said first means includes: h. a first shaft that extends outwardly from said first counterweight and a second tubular shaft that extends outwardly from said second counterweight away from said first shaft and that envelopes at least a part of said drive shaft; and i. first and second bearings rigidly supported from said first and second side pieces that rotatably support said first and second shafts, with said first shaft rotating at a different rate of rotation than said drive shaft.

3. A device as defined in claim 1 in which said first means includes: h. a first shaft coaxially aligned with said drive shaft; i. key means for removably connecting said first shaft to said drive shaft, with said drive shaft and first shaft having portions thereof extending through transversely aligned openings in said counterweight; and j. first and second bearings supported from said first and second side pieces, with said first and second bearings rotatably supporting said first shaft and said drive shaft.

5. In combination with a cylinder defining member, a piston slidably supported in said cylinder, said piston including a wrist pin, a hollow case connected to said cylinder defining member, said case including first and second side pieces, a first drive shaft rotatably supported in said case, a device for selectively transforming reciprocating movement of said piston to rotary motion of said piston to rotary motion of said drive shaft or rotary motion of said drive shaft to reciprocating movement of said piston, said device including: a. a connecting rod that has first and second end portions, said first end pivotally connected to said writs pin, said second end portion disposed in said case, with said second end portion in the form of a ring that has an internal diameter substantially greater than the diameter of said drive shaft, and said shaft extending through said second end portion; b. an internal gear rigidly secured to the interior of said second end portion; c. a drive gear rigidly secured to said drive shaft said drive gear situated in said case and within the confines of said internal gear, but not in toothed engagement with the latter; d. two laterally spaced first and second counterweights that include outwardly extending first and second gear carrier portions that are disposed in said case on opposite sides of said second portion of said connection rod; e. first means that rotatably support said first and second counterweights and carrier portions in said case to revolve about the longitudinal axis of said drive shaft; f. second means for holding said first and second counterweights and carrier portions in predetermined lateral spacing; and g. at least one planetary gear rotatably supported between said first and second gear carrier portions and in toothed engagement with said internal gear and said drive gear, with the centers of rotation of said drive gear and planetary gear being coaxially aligned on the longitudinal axis of said connecting rod when said piston is a maximum distance from said drive shaft, with the distance between the centers of rotation of said drive gear and planetary gear being the length of the stroke of said piston as said drive shaft rotates, with the throw of said planetary gear being twice said stroke as said counterweights and gear carrier portions rotate about the center of rotation of said drive gear, and the number of rotations said drive shaft makes for each complete reciprocating cycle of said piston being the ratio of the internal tooth diameter of said internal gear to the tooth diameter of said drive gear plus one.