Internal combustion engine

Oct 23, 1934.

e: GRAY 1,978,194

INTERNAL COMBUSTION ENGINE Filed Feb. 24, 1931 3 Sheets-Sheet 1

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Oct. 23, 1934. _{E GRAY} 1,978,19'

INTERNAL COMBUSTION ENGINE

Filed Feb. 24, 1931 3 Sheets-Sheet 2

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'ATTORNEYS

Oct. 23, 1934.

1,978,194

E. GRAY

INTERNAL· COMBUSTION ENGINE

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Patented Oct. 23, 1934

1,978,194

UNITED STATES PATENT OFFICE

1,978,194

INTERNAL COMBUSTION ENGINE

Edward Gray, Detroit, Mich., assignor to Edward Gray, Engineer, Inc., Detroit, Mich., a corporation of Michigan

Application February 24, 1931, Serial No. 517,876

Claims. (Cl. 123—58)

The present invention pertains to a novel internal combustion engine designed particularly to operate by the direct or solid injection of oil or on a modified Diesel principle.

The object of the invention is to provide a simple and efficient construction in an engine of this type having opposed pistons in each cylinder. In keeping with this object, the cylinder assembly consists essentially of a circular series of separate cylinders held by two end housings. The end housings constitute heads which comprise a part of the cooling system and also carry the means for admitting air and exhausting the burned gases. The flow from the cylinders to these means is governed by the position of the pistons in each cylinder. . .

The reciprocating motion of the pistons is converted into rotary motion of the shaft through the medium of swash disks disposed at an angle to the shaft. On the power stroke of the pistons the disks have a tendency to elongate and bend the shaft. Another object of the invention is to free the shaft from this action of the disks and is accomplished by inserting between the disks a member which permits an initial tension being put on the shaft in such a manner that bending and elongating are prevented.

The invention is fully disclosed by way of example in the following description and in the ac36 companying drawings, in which—

Figure 1 is a longitudinal section of an engine constructed according to the invention,

Figs. 2, 3 and 4 are sections on the lines 2—z, 3—3 and 4—4 of Figure 1;

Fig. 5 is a section on the line 5—5 of Figure 3

Fig. 6 is an elevation of a modified construc^ti°Figs. 7 and 8 are respectively a plan view and vertical section of a modified universal jomt;

Figs 9 and 10 are respectively a plan view and vertical section of another universal joint; and

Figs. 11 and 12 are respectively a vertical section and plan view of still another form of umver^SaReference to these views will now be made by use of like characters which are employed to designate corresponding parts throughout.

The cylinder and water jacket assembly consists of a central assembly of separate cylinders ⁵⁰ and two end members or housings 2 and 2 as may be seen more clearly in Figure 1. The central assembly consists of cylinders 3 arranged in a circular series. Around the central portion of each cylinder is formed a concentric wall 4 spaced ⁵⁵ from the cylinder wall to form a. water jacket 5.

It will also be seen in Figure 1 that the wall 4 is considerably shorter than the cylinder 3 which it surrounds and in fact occupies a position midway between the ends of the cylinder^ ₍

The housings 2 and 2' are of substantially similar construction and may therefore be described together. The inner ends of the housings overlap the ends of the cylinders and are formed with bosses 6 and 6' to receive the cylinders. Each ₍housing moreover has a central boss 7, the center of which is the center of the circular series of bosses 6 and 6'. The inner ends of the housings abut the ends of the cylinders 3 as shown in Figure 1. The assembly is maintained by a sleeve 8 passed through the bosses 7 and having its ends equipped with nuts 9 which are tightened against partitions 10 and 10' within the housings at the outer ends of the bosses 7, whereby the housings are clamped inwardly against the central assembly of separate cylinders.

The housing 2 has another partition 11 between its inner end and the partition 10. Both partitions obviously are apertured for the passage of the cylinders 3 therethrough. The partition 11 forms a water space 12 at the mner end of the housing 2, and this space is brought into communication with the water space 5 of the member 1 by coincident ports 13 formed in the abutting ends of these parts. The partitions10 and 11 form an air chamber 14 at one end of the cylinders and in communication therewith through ports 15. Suitable intake ports16 to> the chamber 14 are provided preferably at diametrically opposite points in the outer wall of the hous ; -ing 2 as shown in Figures 1 and 3.

The partition 10' also forms a water space 17 around the cylinders 3, and this space is also brought into communication with the space 5 by coincident ports 18 formed in the abutting parts of the members 3 and 2'.

The bosses 6' have a channel formation 19 lying outwardly of the bosses or between the bosses and common to all the bosses. The base of this channel structure forms a ring 20 concentric with the boss 7 as may be seen m Figure 2 At two points, the side walls of the channel converge outwardly at 21 to two diametrically opposite exhaust ports 22 in the outer wall of the housing 2'. Communication for exhaust from the cylinders 3 to the channel 19 is provided by ports 23 in the cylinder wails of the channel.

An inner circular wall 24 is formed across the exhaust channel 19 at a short distance inwardly of the outer wall of the housing 2' to form a water space 25 affording communication between

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1,878,194 the parts of the water space 17 at opposite sides of the channel. The wall 24 is of course interrupted at the exhaust ports 22 and there joined as at 26 to the outer wall t»f the housing 2'. '5 A water inlet 27 and an outlet 28 are provided respectively at the bottom of the housing 2 and the top of housing 2', in communication with the spaces 17 and 12 respectively as shown in Figure 1. Due to the diagonal relation of the ZO inlet and outlet with respect to the cylinders, the cooling water must flow parallel to the cylinders in passing through the cooling system. The paths from the inlet 27 through any one of the water jackets 5 to the outlet 28 are equal, 15 and there will therefore be an equal distribution or flow of water among the jackets 5.

Each of the cylinders 3 contains a pair of opposed pistons 30 equipped with outwardly extending connecting rods 31 which in turn are 20 geared to a power shaft as will presently be described. End plates 32 are secured to the outer ends of the housings 2 and 2' and formed with suitable bearing structures 33 in which is journalled a power shaft 34.

The reciprocating motion of the connecting rods 31 is converted into rotary motion on the shaft 34 by means of swash disks 35 surrounding the shaft at an acute angle and splined thereto as at 36 beyond the outer ends of the cylinders

Each such disk is surrounded by a ring structure comprising two parts 37 and 38 threaded one into the other, with ball bearings 39 between the ring and the disk. The function of the ring is merely to carry ball members 40 for providing 35 a universal joint with the connecting rods 31.

The outer end of each rod is formed with a spherical socket 41 receiving a portion of one of the balls 40, and the joint is completed by a spherical cap member 42 fitted on each ball 40 and bolted as at 43 to the corresponding socket member 41. Inasmuch as the reciprocation of the connecting rods cannot pull or push the disks 35 in the direction of piston travel, the rings 37, 38 are compelled to change their angular 45 position relatively to the shaft 34, which is permitted only by rotary movement of the disks on their centers. This movement results in rotation of the shaft since the disks are splined to the shaft.

Each cylinder is equipped with a nozzle 44 approximately midway between its ends. This nozzle is constructed to spray a charge of atomized fuel into the space between the pistons when the latter have reached their minimum spacing 55 compressing a quantity of air therebetween.

At this time, the temperature of the compressed air is sufficient to ignite the mixture of air and sprayed fuel, whereupon an expansion or senalation of the pistons follows in accordance with 60 the Diesel principle of operation.

The pistons in separating produce a strain in the disks 35 which tends to elongate and bend the shaft 34. In order to overcome this tendency, a compression member or sleeve 45 is mounted 65 around the shaft between the disks 35. The ends of the sleeves are thickened as at 46 to fit snugly around the shaft, while the intermediate part of the sleeve is spaced from the shaft. The ends 46 are abutted by hubs 47 formed as part 70 of the disks 35. The outer end of one of the hubs bears against a stop collar 48 on ths shaft 34. The outer end of the hub of the other disk is engaged by a nut 49 threaded on the shaft: This nut is adjusted to bind the disks against 75 the sleeve 45.

The pushing action of the connecting rods 31 on the disks 35 tends to rock the latter about the ends of the members 45 and thus to elongate the shaft 34 by the outward force against the members 48 and 59. To overcome this tendency, 8ft the shaft is placed in a condition of initial tension by sufficient tightening of the nut 49. The intermediate parts, namely the sleeve 45 and hubs 47, are of sufficiently low compressibility to resist the reaction of the tension in the shaft and 85 to maintain the shaft in its condition of initial tension. The magnitude of this tension is greater than the tension or elongation effect produced upon the members 48 and 49 through the connecting rods and hubs of the disks as described, 90 and hence the latter tendency is ineffective on the shaft.

In order to prevent rotation of the rings 37, 38 with the disks 35, each of the housings 2 and 2 is formed with a track 2α extending length- 95 wise of the shaft 34 and curved about the center of oscillation of the corresponding disk 35. Each ox the rings has a stem 37α extending therefrom on which is slidably mounted a block 37b received in the track to move therein. By this 100 means, the rotation is confined to the disks 35 and shaft 34.

By reason of the splined mounting of the disks 35 on the shaft 34, either disk may be advanced or retarded with respect to the other so that they 105 will be unsymmetrical with respect to a vertical plane passed transversely through the cylinders 3. To make such an advancing or retarding adjustment the nut 49 is removed and the connecting rods 31 are removed from the balls 40. no The swash disk 35 is then slipped off the splines 36 and is rotated slightly while the shaft 34 remains stationary, and it is then replaced on the splines, the nut 49 is replaced, and the connecting rods re-assembled on the balls 40. If the v.5 disk within the housing 2', for example, is advanced, a piston connected thereto will close the exhaust ports 23 of the corresponding cylinder before the air admission ports 15 in the samp cylinder are closed. This will result in super- 20 charging of the cylinder with compressed air.

In the modification shown in Figure 6, the water jackets are replaced by cooling fin’s 50 formed exteriorly on the cylinders. The air intake channel and the exhaust channel are built up from the cylinders as indicated by the numerals 51 and 52.

Figures 7 to 12 inclusive illustrate various other constructions for providing a universal connection between the connecting rods and the i-m swash disk rings. In Figures 7 and 8, the ring ' is formed in two parts 53 and 54 secured together by a bolt 55. The part 53 is formed with an upstanding lug 56 through which is passed a pin 57. A ring 58 surrounds the pin and has ->₅bearings 59 in which the ends of the pin are received. The ring further has a peripheral groove 60 in which is mounted a spring ring 61. The connecting rod 62 has its outer end formed as a ring 63 adapted to be fitted over the ring · 58 when the spring ring 61 is compressed in the groove 60. The ring 63 has an inner groove 64 adapted to register with the groove 60, whereupon the spring ring 61 enters partially into the latter groove to hold the parts together while permitting relative rotation therebetween on an axis perpendicular to that of the pin 57. To separate the rings 58 and 63, screws may be turned in tapped holes 63’ in the outer ring until the spring ring 61 is forced entirely into 15c

1,978,194 3 ing said shaft between said disks and engaged thereby, and means on said shaft engaging the outer sides of said disks and holding said shaft under initial tension.

3. An internal combustion engine comprising parallel cylinders, a shaft between said cylinders and parallel thereto, a pair of opposed pistons in each cylinder, a pair of swash disks on said shaft at the ends of said cylinders, a ring rotatably mounted on each disk, connecting rods extending from said pistons and having universal connections with said ring, a sleeve surrounding said shaft between said disks, and means binding said disks against the ends of said sleeve and holding said shaft under initial tension.

4. An internal combustion engine comprising parallel cylinders, a shaft between said cylinders and parallel thereto, a pair of opposed pistons in each cylinder, a pair of swash disks on said shaft at the ends of said cylinders, connecting rods extending from said pistons and joined to said disks, means for holding said disks in spaced relation, and means engaging said disks for holding said shaft under initial tension.

5. An internal combustion engine comprising the groove 60, after which the outer ring may be withdrawn.

In the construction shown in Figures 9 and 10, the ring surrounding the swash disk also comprises two parts 65 and 66 tied together by a bolt 67. The part 66 is formed with a pair of spaced ears 68 between which is journalled a block 69 on trunnions 70. The block also has trunnions 71 extending therefrom on an axis perpendicular to that of the members 70. The connecting rod comprises two similar pieces 72 bolted together at 73 and formed each with an offset portion 74 at each end to provide forks adapted to be journalled on the trunnions 71 and on a similar block 75 journalled in the piston 76. Thus, a universal joint is provided between the piston and the rod and between the rod and the swash disk ring.

In the modification shown in Figures 11 and 20 12, the swash disk ring consists of two parts 77 and 78 bolted, together at 79. The connecting rod 80 has its outer end formed with a ball 81 received in a socket 82 into which the ball 81 is mounted prior to the application of the sec25 tion 77. The latter has a like socket 83 engaging -. — , the ball and thereby preventing.it from being parallel cylinders, a shaft between said cylinders withdrawn in any direction. The section 78 has and parallel thereto, a pair of opposed pistons a slot 84 communicating with the socket 82 there- in each cylinder, a pair of swash disks on said of. When it is desired to remove the ball from shaft at the ends of said cylinders, a ring rothe swash disk ring, the section 77 is released tatably mounted on each disk, connecting rods and withdrawn. The ball 81 is also withdrawn extending from said pistons and having uniin the same direction, and after it has been re- versal connections with said ring, means for moved from the socket 82, the rod 80 may be holding said disks in spaced relation, and means passed through the slot 84. . engaging said disks for holding said shait under

Although specific embodiments of the inven- initial tension.

tion have been illustrated and described, it will 6. An internal combustion engine comprising be understood that _;various alterations in the parallel cylinders, a shaft between said cylinders details of construction may be made witho.ut de- and parallel thereto, a pair of opposed pistons parting from the scope of the invention, as indi- in each cylinder, a pair of swash disks on said 49 cated by the appended claims. shaft at the ends of said cylinders, connecting jjg