JPS6014921B2 - Rotary power transmission device - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention utilizes hydraulic or pneumatically actuated cylinders and actuators to provide rotational action in which continuous power is maintained without an impact or abrupt stop at the end of the stroke of a piston within the cylinder. It relates to a transmission device.

When using hydraulic or pneumatically actuated cylinders, it is common to provide power to the transmission using a solenoid actuated valve or a spring loaded valve to control fluid flow to the cylinder.

This results in a significant momentary stoppage of the piston at the end of each stroke within the syringe, resulting in a momentary stoppage being transmitted throughout the transmission, increasing maintenance costs as well as overloading the device parts. Fatigue has been observed. The present invention utilizes a pair of hydraulically or pneumatically actuated cylinder-piston devices, preferably located at a nine-point angle around the working axis of the device in a housing in which the crankshaft is mounted, with the piston rods of both cylinders Connected to the common crank pin of the crankshaft.

The two cylinders are each provided with a trunnion supported at its inner end in a bearing on the outer wall of the housing, the wall of said housing being notched to permit rocking movement of the piston rod of the cylinder-piston arrangement. It is provided. The crankshaft to which the piston rod is connected has an extension with a force take-off at one end. In the illustrated form, the force take-off is a chain sprocket wheel. The opposite end of the crankshaft is 18
A pair of levers has an extension located at right angles to the axis of the shaft at an angle of 0o. These levers terminate in rollers that are in operative contact with cams on each of a pair of valves that control the flow of fluid to the hydraulic or pneumatic cylinder of the cylinder-piston arrangement. It is desirable to locate the cylinders at nine-point angles to each other to maximize operating efficiency. However, under certain special conditions, the cylinders are 45
They can be spaced apart as narrow as 0 or as large as 1350 degrees and still provide effective operation. For the 18-pin setting of the lever on the crankshaft, the control valves are installed at a 90° angle, and the cam on each control valve is centered over the center of the cylinder it controls.

The connection of the two piston rods to the crankshaft crankpin is such that when the piston in one cylinder is at one end of that cylinder, the piston in the other cylinder is at an intermediate point within the cylinder. With this configuration, the midpoint piston in one cylinder exerts the greatest force relative to the position of the piston in the other cylinder to rotate the crankshaft over dead center, thus creating a continuous rotational movement of the crankshaft. This eliminates the problems caused by shock and momentary stopping of the piston at the end of its stroke. A rotary power transmission device using a pair of cylinder-piston devices and a servo valve is known from British Patent No. 1,323,065, published 11 King July 1972.

In this patent, rotational motion is imparted to the input shaft and crank plate. The cylinder piston device is located between the input crank plate and the output crank plate/output shaft. A servo valve is mounted on the cylinder piston arrangement, the servo valve being actuated by the input crank plate, and the piston rod of the cylinder piston arrangement being operatively coupled to the output crank plate. This device relies on a small amount of input shaft momentum relative to the output shaft to create a servo-valve action resulting in fluid flow to the Schilling piston device to impart rotational motion to the output crank plate and output shaft. It is an object of the present invention to provide a rotary power transmission device that uses hydraulically or pneumatically actuated cylinders to ensure continuous power drive operation.

Another object of the invention is to provide a rotary power transmission device in which a pair of cylinder-piston devices are operated in such a manner as to eliminate shocks or momentary stops at the end of the stroke of the piston in each cylinder. .

Yet another object of the invention is to control the flow of fluid to the cylinders of a pair of cylinder-piston devices so that the pistons at the end of their stroke when the crank of the device is in a dead center position with respect to the axis of the cylinders. A pair of valves controls fluid flow to the cylinders of the cylinder-piston device in a timed sequence to cause movement of the piston and piston rod of the device in a manner that eliminates shocks or momentary stops. The present invention provides a rotary power transmission device including an actuator mechanism.

Another object of the invention is that a pair of hydraulically or pneumatically actuated cylinder piston devices are mounted on the trunnions of the crankcase, and the piston rods of the devices are coupled to a common crank pin of the crankshaft of the device. The purpose of the present invention is to provide a rotary power transmission device.

Another object of the invention is to provide a rotary power transmission in which a separate control valve in the fluid circuit for the Schilling piston device allows the drive output of the transmission to be reversed without impacting the device. be.

These and other objects of the present invention will become apparent upon consideration of the accompanying drawings and the following description. The attached drawings, especially the first
5, the rotary power transmission device 5 includes a crankcase 6, a control valve housing 7 mounted on the crankcase 6, a pair of hydraulically or pneumatically operated cylinder pistons 8, 9, the cylinder piston device is pivotally mounted on the side surface of the crankcase 6 and is arranged at an angle of 900 with respect to the axis of the crankshaft 10. The cylinder piston devices 8 and 9 are fitted with a trunnion 11, and the side wall portion 13 of the crankcase 6
A pair of brackets 12 attached to the cylinder allow rocking movement of the cylinder.

The wall surface 13 is provided with a cutout as shown at 14 between the pair of brackets 12, so that each cylinder 8,
Piston rod 15 is swung relative to 9. Attached to the crankcase 6 is a monoscopic crankshaft 10 rotatable within bearing rigs 16 located on the top and bottom walls 17 and 18 of the crankcase.

The crankshaft 10 has an upper shaft 19, a lower shaft 20, and a pair of crank webs 21 integrally connected by a crank pin 22. Piston rod 1 of cylinder 8
5a terminates at the outer end of a fork-shaped clevis 23 which rests on the crankpin 22.

The piston rod 15b of the cylinder 9 terminates in a clevis 24 which is also supported on a crank pin 22 between the fork portions of the clevis 23 of the piston rod 15a. The lower output shaft 20', in this embodiment, the chain drive section 2
6 and terminating in a sprocket wheel 26 which engages with the sprocket wheel 26. However,
It should be understood that the sprocket wheel 25 could be replaced with other forms of force take-off, such as a lever or gear system. Upper shaft portion 19 of the crankshaft 10
has an axial extension shaft 27 extending into the control valve housing, the upper end of which rests on a support bar 28 located directly below the hinged cover 29 of the housing 7. .

In the configuration shown in FIGS. 2, 4, and 5, the extension shafts 27 extend outwardly at right angles to their axes and are spaced from each other at 180° intervals around the axes of the shafts 27. a pair of valving arms 30 positioned in spaced relationship;
31 is provided.

Each of these working arms 30, 31 is adjustably screwed onto the shaft 27 and secured in its adjusted position by a lock nut 32. A pair of control valves 33 and 34 are mounted on a plate 35 fixed to the outer surface of the side wall 7a of the housing 7, said valves projecting into the housing via a closure 36.

Shims 37 are inserted between the plate 35 and the side wall surface of the housing 7 to adjust the valves 33 and 34 relative to the rollers 38 at the ends of the arms 30 and 31 and the center of the shaft 27.
Each valve 33 and 34, preferably of the spool type, has an operating shaft 3.
9, and a cam 40 is attached to this operating shaft.

Each cam 40' has two cams disposed diagonally opposite each other.
A pair of concave cam surfaces 41 and a pair of partially cylindrical cam surfaces 42 are provided diagonally opposite from each other between each cam surface 41 . These cam surfaces 41 are contacted by rollers 38 on arms 30 and 31 when crankshaft 10 is rotated, thus causing rotation of the spools of valves 33 and 34 and causing cylinder pistons 8 and 9 to rotate as described below. Controls fluid flow to each cylinder. Control valves 33 and 34 have cam surfaces 41 whose operating cams 40 are located within the vertical spacing between arms 30 and 31, as shown in FIGS. 1 and 5, so that cam surfaces 41 are located in opposite directions. housing 7 at an angle of 9 degrees in such a positional relationship that the arms 30 and 31 are contacted by the rollers 38 of each arm 30 and 31 as the arms rotate with the rotation of the crankshaft 10.
located within.

The axis of the cam 40 is tapered so that it is aligned with the center of the trunnions 11 of the cylinder-piston devices 8 and 9, as shown in FIG. In Figures 8 and 9,
An example of a modification of the valve control device is shown. In this variation, the shaft 27a has a square cross-sectional portion 43 and a small diameter extension 44 centered on a bearing 45 located on the support bar 46. The shaft 47 is an extension shaft 27a
It passes through the square cross section 43 of the head 48 at one end.
It also has a threaded portion at the other end to receive a lock nut 49. a pair of U-pins 50 each having a block 52;
and 51' are supported on shaft 27 on either side of portion 43 of extension shaft 27a.

Attached to each of the blocks 52 is a short shaft 53, at the outer end of which is fitted a cam 40 for controlling valves 33 and 34 in the manner shown in FIGS. A roller 54 is supported for contacting the cam surfaces 41, 42. Attached to the lower end of portion 43 of extension shaft 27a are a pair of arms 55 extending outwardly in opposite directions.

L to align roller 54 with cam 40 of valves 33 and 34.
Each U-link 50 and 51 is screwed into a block 52.
An adjustment device having a pair of screws 56 is provided.

The lower end of the screw 56 is rounded and rests against the upper end of the arm 55. The screw 56 is locked in its adjusted position by a lock nut 57. The clevises 50 and 51 further connect the screw heads 59 to the adjustment surfaces 6 of the blocks of the clevises 50 and 51.
It is fixed relative to the extension shaft 27a by an adjusting screw 58 which is screwed into the part 43 of the extension shaft 27a in contact with 0 and fixed in its adjusted position by a lock nut 61. In this manner, each roller 54 can be adjusted to rotate in smooth contact with the cam surfaces 41 and 42 of the cam 40.

In the configuration shown in FIGS. 8 and 9, as shown in FIGS. 4 and 5, the operating tree 3 of the valves 33 and 34 is
9 is arranged horizontally, and the cam 40G of the shaft 39 rotates within a vertical plane.

In the further modified configuration shown in FIGS. 10 and 1, control valves 33a and 34a are
It is mounted within the housing 7 in the same manner as shown in FIGS. 1, 2, and 4, except that the operating shaft 62 of the cam 40a projects upward at a right angle and the cam 40a rotates in a horizontal plane.

An extension shaft 63 extending upwardly from the crankshaft 10 is supported by a plate 64 which is further secured to a support block 65 by screws 66.

Attached to the upper end of the extension shaft 63 is a block 67 having a rectangular entrance 68 that penetrates the extension shaft 63 in a direction perpendicular to its center. A pair of arms 69 and 70 are secured within the closure 68 by a locking stud 71 and extend outwardly from each other in diametrically opposite directions.

The radius of the arm 69 from the bag center of the shaft 63 is shorter than the radius of the arm 70. Supported vertically at the outer end of each arm 69 and 70 is a downwardly extending short koji 72, with a loaf 73 of each short shaft 72 in contact with a cam 40a of each valve 33a and 34a. supported on the lower end. As shown in FIG. 11, when arms 69 and 70 are rotated in the direction of arrow A, arm 70 has a relatively long radius.
The roller 73a contacts the concave surface 41 of the cam 40a radially away from the center of the shaft 63, and the cam 40a and the valve 3
By rotating the spool 4 counterclockwise, the roller 73b of the short diameter arm 69 is released from contact with the cam of either valve.

This further rotation of the arms 69 and 70 in the direction of arrow A causes the roller 73a of the longer arm 70 to move onto the shaft 63.
The cam 40b is brought into active contact with the concave surface 41 of the cam 40b, which is radially distant from the edge of the cam 40b, and the cam 40b and the spool of the valve 32a are rotated in the counterclockwise direction.

Further rotation of arms 69 and 70 brings roller 73b of short radius arm 69 into operative contact with the concave surface 41 of cam 40a that is radially closest to the center of shaft 63, causing the spool of cam 40a and valve 34a to Rotate clockwise.

Similarly, as arm 69 rotates further, its roller 73
b contacts the concave surface 41 of the cam 40b that is radially closest to the axis of the shaft 63, and the cam 40b and the valve 33a
Rotate the spool clockwise. valves 33a and 34a
The opening and closing sequence, and therefore the alternate inflow and outflow of fluid with respect to the cylinder-piston devices 8 and 9, is maintained to produce a smooth rotational movement of the crankshaft 10.

In a further embodiment shown in FIGS. 12 and 13, the arrangement is similar to that shown in FIGS. The configuration is similar to that shown in Figure 11.The extension shaft 74 has a flat upper part 75 having a square cross-section entrance 76 passing through it in a direction perpendicular to the center of the shaft 74.A pair of arms 69a and 70a. is fixed inside Sekiguchi 76.

Each arm 69a and 70a supports a short shaft 72a, with a roller 73a of the short shaft 72a in operative contact with the concave surface 41 of the cams 40c and 40d in the same manner as previously described with respect to FIGS. 10 and 11. Mounted on the bottom end. The operation of the present invention will first be explained in Figures 14A and 14B.
Reference is made to FIGS. 14C and 140, which illustrate the sequence of operation of valves 33 and 34 in the configuration shown in FIGS. 1, 2, and 4. This sequence of operation is also typical of the operation of the valves of the valve actuation variations shown in FIGS. 8 and 9, FIGS. 10 and 11, and FIGS. 12 and 13. In FIG. 14A, as can be seen from FIGS. 1 and 4, the upper valving arm 31 moving in the direction of arrow A and its roller 38 contact the concave surface 41a of the upper half of the cam 40, causing the cam to move in the direction of arrow A. The cam 40 is attached to the shafts 39 of the spool valves 33 and 34 as shown in FIG. 1 to rotate the spools of the valves counterclockwise.

Further rotation of cam 31 and its roller 38 rotates the cam to the position shown in FIG. 14B, after which roller 38 releases contact with cam 40 and rotation of the valve spool ceases. As extension shaft 27 continues to rotate, roller 38 on lower working arm 30, which moves in the direction of arrow B as shown in FIGS. 1 and 4, moves cam 4 as shown in FIG. 14C.
The cam 4'0 contacts the concave turtle lb in the lower half of the cam 4'0
Rotate clockwise toward the position shown in Figure D, thereby reversing the rotation of the valve spool. Thus, as the extension shaft 27 rotates, each of the valves 33, 34 sequentially rotates its spool in one direction and then in the opposite direction to control fluid flow into and out of the cylinder piston devices 8, 9.

Next, with respect to the fluid circuit diagram shown in FIG. 19, in the schematic diagrams shown in FIG. 15, FIG. 16, FIG. Ten crank pins 22 and piston rods 15 are shown in four 90° inlay positions around the crankshaft center, with pistons 8a and ga at each position within each cylinder of cylinder-piston arrangements 8 and 9.

The arrows shown next to each of the cylinders 8a and 9a indicate the direction of movement of the pistons 8a, ga within each cylinder. In each case, the piston in one cylinder approaches the end of its stroke in one direction, and the piston in the other cylinder moves in the opposite direction so that the crank moves to a certain position, especially when one piston rod is relative to the crank. When the piston in the other cylinder is near dead center, the piston in the other cylinder is at a position within that cylinder that exerts the greatest effect to pull the crank past the dead center relative to the other piston rod. Thus, during a complete 360° rotation of the crankshaft, there is a continuous force transmitted from the output end of the crankshaft to the sprocket wheel 25 and the chain drive 26. In FIG. The valve 77 is set to control the direction of rotation of the device in one direction - the crankshaft is at bottom dead center with respect to the cylinder piston device 8, and the piston 8a is also at bottom dead center with respect to its cylinder 8c. It will be seen that the piston 9a is located halfway within its cylinder gc of the cylinder piston arrangement 9.

The boats A2, B3 and T2 of both valves 33 and 34 are centered with respect to each other in order to avoid a momentary hydraulic blockage in the cylinder during the turning point of the working stroke of cylinders 8 and 9 relative to the crankshaft 10. connected in position. Boats P, T, and T2 of valve 33 open when the valve spool is rotated in the manner previously described with respect to FIGS. 14A, 14B, 14C, and 14D.

When these boats P, T, and T2 are closed, fluid is forced to flow from the pump P through the boats P, 1 to the top 9a of the cylinder 9, and from the bottom of the cylinder 9 through the boats B-T. Return to Tank T. Boat T with valve 34,,
P, and P2 are the crank 10 as shown in Figure 9.
is momentarily closed while the crank pin 22 of the cylinder is at the bottom of its stroke relative to the cylinder, allowing fluid to flow from the bottom 8c of the cylinder 8 back to the tank T via the boat pipe T2 of the valve 84. The flow from the passage through valve 3 is blocked at boat P2.

Valve actuation arm 31 with roller 38 has already been engaged with the concave surface 4 on the top of cam 40 of valve 34 to move the cam in the direction of rotation of arm 31 and thereby move the valve spool in a counterclockwise direction. The spool boats P2 and T2 are connected to flow the fluid from the pump P to the top of the cylinder 8c. The same action of directing fluid from pump P to cylinder gc is effected by first arm 3Q and its roller 38, then arm 3Q and its roller 38.
3 and causes a flow of fluid to the top and bottom of the cylinder g.

When using the valve configuration shown in Figure 1, the connected boat T278 avoids instantaneous stagnation of hydraulic pressure during the changeover, thus preventing shocks in the system.

Also, when the fluid inlet of one of the valves 33, 34 is momentarily closed, the full displacement of the pump acts on the cylinder controlled by the other valve, thereby producing a smoother rotational movement in the output shaft. This means that the speed and torque increase instantaneously.

[Brief explanation of the drawing]

FIG. 1 is a plan view of an embodiment of the present invention showing the control valve and the device for actuating the control valve when the top cover of the valve housing of the rotary power transmission device is opened; FIG. FIG. 3 is a cross-sectional view of the device taken along line 2-2 in FIG. Enlarged longitudinal sectional view of 5th
The figure is a plan view of the device shown in FIG. 4, FIG. 6 is an enlarged front view of the cam attached to the working spool of the control valve, FIG. The figure is an enlarged side view of a modified example of the control valve operating device shown in Figure 1, and Figure 9 is an enlarged side view of a modified example of the control valve operating device shown in Figure 1.
Plan views of the valve actuation device shown in Figures 10 and 11.
The figures are a longitudinal cross-sectional view and a plan view of yet another modification of the valve actuation mechanism, respectively, FIGS.
Fig. A, Fig. 14B, Fig. 14C, and Fig. 140 are operational views of the roller and cam that control the valve directly installed, Fig. 15
16, 17, and 18 are views showing the four-quadrant positions of the piston, piston rod, and pivotally mounted cylinder of the crankshaft of this device, and FIG. 5 is a fluid circuit diagram for the present device and hydraulic or pneumatic actuation, including a valve actuation device provided in the present invention. 8, 9... Cylinder piston device, 10... Crankshaft, 15.
... Piston rod, 19 ... Upper shaft, 20 ... Lower shaft, 21 ... Crank web, 22 ... Crank pin 23, 24 ... U link, 25 ... Sprocket wheel, 26... Chain drive section, 27... Extension shaft, 30, 31
... Valve actuation arm, 33, 34... Control valve, 40... Cam, 41, 42... Cam surface. 'J.G. 'FJG2 〆'G3 'JG4 Bang G5 attached G6 ''G7 'rG8 ''G9 F'G'○ F'G. 〃F'G. Boen G. '3 F'G. Ko F'G. '4c F'G. '4b F'G. '4d 〆JG'5 f'G. /6 〆rG'7 'SoG'8 F'G. '9

Claims (1)

[Claims] 1. A transmission shaft with a single-headed crank located in a crankcase, the shaft having a power take-off device at one end and an extension shaft that acts on a valve at the other end. a pair of double-acting cylinder-piston devices pivotally mounted on the outside of the crankcase, each of the cylinder-piston devices having a piston rod supported by a crank pin of the crankshaft; a pair of valves each controlling fluid flow to one cylinder of the piston arrangement; a pair of arms on an extension shaft for actuating said valve; and a cam contact roller on each of said arms; are sequentially opened and closed by said roller engaging said cam, rotating said cam to control the flow of fluid from said valve to said cylinder, causing rotation of said crankshaft by said piston rod, and one side of said cylinder-piston arrangement. A rotary power transmission device characterized in that the piston rod of the cylinder piston device is actuated to rotate the crankshaft beyond the dead center when the other piston rod of the cylinder piston device is at the dead center with respect to the crankshaft. 2. The rotation according to claim 1, wherein the cylinder of the cylinder-piston device is pivotally attached to the crankcase, and the piston rod of the crank-piston device passes through a notch in the crankcase. Power transmission device. 3. The rotary power transmission according to claim 1, wherein the paired cylinder-piston devices are pivotally mounted on the crankcase at intervals of 90 degrees around the axis of the crankshaft. Device. 4. The rotary power transmission device according to claim 1, wherein the piston rod of each cylinder piston device has its outer end supported by a crank pin of the single-head crankshaft. 5. Said pair of valves are spool-shaped, said cam being fixed on the working axis of said spool, and said working shaft and spool being on an axis perpendicular to the pivot axis of the cylinder of said cylinder-piston device. 2. The rotary power transmission device according to claim 1, wherein the rotary power transmission device is arranged in a rotary power transmission device. 6. The rotary power transmission device according to claim 1, wherein the rollers in contact with the arm and the cam are arranged at intervals of 180° around the axis of the valve action extension shaft. 7. The rotation of claim 6, wherein the arm is adjustably screwed onto the valve action extension shaft for aligning the roller with respect to the cam and is fixed in the adjusted position. Power transmission device. 8. said cams each having a pair of diametrically opposed concave cam surfaces, and a roller on said arm of said valve action extension shaft contacts said concave cam surfaces to control the cam of the valve. 2. The rotary power transmission device according to claim 1, wherein the rotary power transmission device generates rotational motion to control inflow and outflow of fluid with respect to the cylinder piston device. 9. The rollers with which said pair of arms and cams contact are located axially spaced from each other on said valving extension shaft, and one roller of said pair of arms contacts one concave surface of said each cam. the other roller of the pair of arms contacts the other concave surface of each of the cams to sequentially rotate the cams in opposite directions;
9. The rotary power transmission device according to claim 8, wherein a fluid flow is generated to the cylinders of said cylinder-piston device in order to sequentially reciprocate the piston rods of said cylinder-piston device. 10 The valve action extension shaft has a short axis extending therethrough at right angles to its axis, a pair of U-links are pivotally connected to the short axis, and the pair of arms and cam contact rollers are One piece is fixed to each of the U links, and the U link is fixed to each of the U links.
2. The rotation according to claim 1, further comprising means for individually adjusting the links with respect to the axis of the valve action shaft and adjusting the rollers with respect to the cam surface of the cam of the valve. Power transmission device. 11 The adjustment device includes a screw device threadedly engaged with each of the U-links to adjust the position of the U-link about the axis of the short shaft, and a screw device threadedly engaged with the valve action extension shaft to adjust the U-link to the short shaft. Claim 10, characterized in that it has a screw device for fixing the shaft in an adjusted position around its axis.
The rotary power transmission device described in . 12. The valving extension shaft has a blocking member at its outer end, the blocking member having a through hole disposed perpendicular to the axis of the extension shaft, and a pair of valve actuating extension shafts mounted within the through hole. 2. The rotary power of claim 1, wherein a roll support arm extends outwardly in an opposite direction from said block member and further includes means for adjustably securing said arm to said block member. transmission device. 13. The valve has its working shaft and cam arranged parallel to the axis of the extension shaft, and the roller engaging the cam is mounted on a short shaft projecting from the ends of the pair of roller support arms. The rotary power transmission device according to claim 12, characterized in that: