US3212483A

US3212483A - Reciprocating machinery

Info

Publication number: US3212483A
Application number: US275012A
Authority: US
Inventors: Vernon W Balzer
Original assignee: Individual
Current assignee: Individual
Priority date: 1963-04-23
Filing date: 1963-04-23
Publication date: 1965-10-19
Anticipated expiration: 1982-10-19

Description

Oct. 19, 1965 v. w. BALZER RECIPROCATING MACHINERY m I. &R N mm 4 m im 3% W mm 04 W Flled Aprll 23 1965 Oct. 19, 1965 v. w. BALZER RECIPROCATING MACHINERY 3 Sheets-Sheet 2 Filed April 23, 1965 1 M ,W a 7 Oct. 19, 1965 v. w. BALZER RECIPROCATING MACHINERY 3 Sheets-Sheet 3 Filed April 25, 1963 NNN -raa4 3 United States Patent 3,212,483 RECIPROCATING MACHINERY Vernon W. Balzer, Star Rte, Whitlock Road, Mariposa, Calif.

Filed Apr. 23, 1963, Ser. No. 275,012 11 Claims. (Cl. 123-41.84)

The present invention relates to reciprocating machinery of the general barrel type disclosed, for example, in Patent 3,007,462 which issued Nov. 7, 1961, in the name of the present inventor, and which includes a central crankshaft and a plurality of longitudinally-extending parallel cylinders angularly positioned around the axis of rotation of the shaft.

Barrel type reciprocating machinery comprises essentially a block, and a central crankshaft journaled in the block. The central shaft has an oblique crank mounted on each of its ends. A plurality of cylinders extends through the block parallel to the axis of rotation of the central shaft, and these cylinders are spaced at equiangular positions around the shaft. A pair of opposed pistons are mounted for reciprocal motion in each of the cylinders. A wabble spider is journaled on each of the oblique cranks, and the pistons in the respective cylinders are coupled to the wabble spiders.

The barrel type reciprocating machinery, such as described briefly above, may be used, for example, either as a compressor in which case the central shaft is driven; or as a power generator, in which case the pistons in the cylinders are driven.

It is an object of the present invention to provide an improved reciprocating machine of the barrel type, which is adapted to be assembled and constructed in an improved and simplified manner.

An object of the invention is to provide such an improved reciprocating machine which can be readily disassembled for repair or replacement of parts.

Yet another object of the invention is to provide such an improved reciprocating machine in which the pistons are configured, and in which the introduction of fuel into the combustion chamber is such, that improved efficiency is achieved and there is little or no tendency for the fuel to be washed along the bores of the cylinders which would serve to dilute the lubricating oil and cause deterioration of the machine.

Yet another object of the invention is to provide such an improved reciprocating machine which includes liners for the various cylinders, constructed in a manner to facilitate their scaling to the block; and also constructed to provide for the convenient formation of intake and exhaus manifolds, cooling cavities, and [the like, in the engine block.

A still further object of the invention is to provide such an improved construction for the reciprocating machine whereby the cylinder liners are retained in the engine block against linear and rotational motion in an improved and simplified manner and with a minimum of restraining components.

A still further object of the invention is to provide such an improved reciprocating machine which incorporates improved coupling means for linking the pistons in the different cylinders to the corresponding wabble spiders.

Other objects and advantages of the invention will become apparent from a consideration of the following description, when the description is taken in conjunction with the accompanying drawings, in which:

FIGURE 1 is a side sectional elevational view of an improved reciprocating machine constructed in accordance with the concepts of the present invention;

FIGURE 1A is a schematic representation, substantially on the line 1A1A, of the spray angle of the fuel fed into each of the cylinders of the machine of FIGURE 1;

3,212,483 Patented Oct. 19, 1965 FIGURE 1B is an enlarged fragmentary view of a portion of the machine of FIGURE 1;

FIGURE 10 is a schematic representation, substantially on the line 10-10 of FIGURE 1A;

FIGURE 2 is a cross sectional view of the machine of FIGURE 1, taken substantially on the line 22 of FIG- URE 1;

FIGURE 3 is an enlarged view of one of the connecting rods of the machine of FIGURE 1, and illustrating in a sectional representation of the manner in which the ends of the connecting rod are coupled to the components linked thereby;

FIGURE 4 is a perspective view of one of the coupling components in the assembly of FIGURE 3;

FIGURE 5 is a perspective view of a threaded nut component untilized in the assembly of FIGURE 3;

FIGURE 6 is a cross-sectional view of a cylinder of the machine, substantially on the line 6-6;

FIGURE 7 is a cross-sectional view of the cylinder, substantially on the line 77; and

FIGURE 8 is a fragmentary view of a portion of the machine, substantially on the line 8- 8 of FIGURE 1.

With reference now to the drawings, and particularly to FIGURE 1, the illustrated reciprocating machine is shown as including an engine block designated generally by the numeral 10. A central shaft 12 extends through the block 10, and the shaft 12 is journaled in the block by means of a pair of bearings 14 and 16 at each end of the block. The shaft 12 includes a pair of oblique cranks 18 and 20 which are preferably formed integral with the shaft, and which extend from the opposite ends of the shaft.

A counterweight member 22 is afiixed to the crank 18, and it serves to link the crank to a stub shaft 24. The

stub shaft 24 is preferably formed integral with the counterweight 22. The stub shaft is axially aligned with the shaft 12.

A counterweight member 26 is affixed to the crank 20, and it serves to link the crank 20 to a drive shaft 28. The drive shaft 28 is preferably integral with the counterweight 22. It is axially aligned with the shaft 12 The stub shaft 24 is journaled in the block 10 by means of a suitable bearing 30, and the drive shaft 28 is journaled in the block by means of a suitable bearing 32. The bearing 30 is mounted in an end bell 34, which, in turn, is mounted on one end of the block 10 by screws 36.

The bearing 32 is mounted in an end bell 38 which, in turn, is mounted on the other end of the block 10 by screws 40. Appropriate gears 42, 44, and 46, of different diameters, for example, are mounted on the drive shaft 28. These gears are used to drive certain auxiliary equipment such as the intake and scavenger blowers, and the lubricating pump. The main load is coupled to the shaft 24 at the opposite end of the engine.

The engine block 10 has a plurality of cylinders 48 extending through it. These cylinders extend through the block in spaced and parallel relationship with the axis of rotation of the shaft 12. The cylinders 48 are spaced equal radial distances from the shaft 12, and are spaced at equi-angular positions around the shaft.

For reasons which will become apparent as the description proceeds, the left hand end of the engine block 10 of FIGURE 1 will be referred to as the exhaust end; and the right hand end of the block will be denominated the intake end.

A plurality of exhaust pistons 50 are respectively mounted in the exhaust ends of the cylinders 48 for reciprocal motion therein. A corresponding plurality of intake pistons 52 are respectively mounted in the intake ends of the cylinders 48 for reciprocal motion therein.

The exhaust pistons 50 are so called because they serve as valves to open and close exhaust ports 54 in the cylinders 48. The intake pistons 52 are so called because they serve as valves to open and close intake ports 56 in the cylinders 48.

The

ports

54 and 56 are each inclined at an angle of, for example, 20 to the axis of the cylinder. This inclination of the ports provides an angular passage for the piston rings to pass over for smooth operation. The intake ports 56 are inclined to the corresponding radial axes by angles of, for example, 30-35 (FIGURE 7), to provide a desired swirling action in the cylinder during the intake and scavenging period. The exhaust ports, on the other hand, are inclined to the corresponding radial axes (FIGURE 6) in a manner to direct the exhaust gases along essentially straight paths to the exhaust manifolds.

A wabble spider 60 is rotatably mounted on the oblique crank 18, and this spider is linked to the several exhaust pistons 50 by respective piston connecting rods 62. The connecting rods 62 are coupled to the spider 60 by ball and socket joints 64, and they are coupled to the respective pistons 50 by ball and socket joints 66.

The oblique crank 20 at the intake end of the engine block 10 is similarly equipped with a spider 68. The spider 68 is linked in a similar manner to the pistons 52.

The engine shown in FIGURE 1 is of the opposed piston type, and it operates basically in known manner, as described in the patent referred to above.

The exhaust and intake pistons 50 and 52 approach each other within each cylinder 48, and they are then pushed apart by the rapid burning and expansion of the fuel injected into the cylinders by the injectors, such as the injector 70, from an appropriate fuel line 72. As noted, a fuel injector, such as the injector 70, is provided for each cylinder 48.

The counterweight 22 is provided with a sloping notch 201 which is deeper at the inner side of the counterweight than at the outer side. The purpose of the notch 201 is to provide clearance for the removal of the piston and piston rod assembly 50-62. In order to remove this assembly, the rod 62 is freed from the spider 60 and then pulled out of the cylinder. The rod 62 can be canted or tilted to some extent, but it would not clear the counterweight 22 normally, except for the provision of the notch 201 in which the rod 62 rides as the assembly is pulled out of the cylinder. When the edge of the piston is pulled against and requires clearance around the counterweight 22, however, the entire piston 50 is pulled free of the cylinder and the entire assembly may be lifted out of the block. A similar notch is provided on the counterweight 26.

In the operation of the machine, as the pistons 50 reciprocate in the respective cylinders 48, a thrust is successively applied to various points on the wabble spider 60. This thrust causes the wabble spider 60 to wabble, and thereby to impart rotation to the crank 18 and to the shaft 24. The wabble spider 60 does not rotate in the operation of the machine, it merely Wabbles around as the oblique crank 18 rotates.

The wabble spider 68, in like manner, imparts rotation to the oblique crank 20. The resulting rotation of the oblique cranks 18 and 20 causes the shaft 12 and the drive shafts 24 and 28 to rotate.

The transmission of torques from the outward thrust of the pistons 50 and 52 produces a torque on the spiders 60 and 68 tending to cause the spiders to rotate. These torques must be resisted so as to protect the piston rods and enable the machine to operate properly.

In order to prevent rotation of the wabble spider 60 while still permitting the necessary wabble action thereof, the spider 60 is linked to the engine block 10 by a pair of spiral bevel gears 74 and 76. The spiral bevel gear 74 is mounted on the spider 60, and the spiral bevel gear 76 is mounted on the block. These spiral bevel gears 74 and 76 mesh with one another during the rotation of the oblique crank 18 and prevent rotation of the spider 60.

A similar pair of meshing spiral bevel gears 78 and are respectively mounted on the spider 68 and on the other end of the engine block 10. These latter bevel gears restrain rotation of the spider 68 while freely permitting the required wabble action of the spider.

Each of the cylinders 48 is equipped with a cylindrical sleeve, or liner, 82. The liners 82 are mounted in place by eccentric rings, so that they are off center with respect to the corresponding cylinder bores, as shown in FIG- URES 1 and 2.

The above-mentioned eccentric mounting rings each have a circumferential groove 84 around its external surface. These grooves serve to contain O-ring seals, and they provide a longitudinal seal between the liners 82 and the inner surface of the corresponding cylinder bore 48.

The engine block 10 is shaped to provide passageways 86 for coolants, such as water. The block is also shaped to provide an intake manifold 88 which surrounds the intake ports 56 in the different cylinders 48 and cylinder liners. The block also is shaped to provide dual exhaust manifolds 90 and 92.

It will be understood that the shape of the block, as mentioned in the preceding paragraph, cooperates with a complementing shape of the various cylinder liners 82, so as to provide the desired passageways and manifolds.

The exhaust ports 54 of half of the cylinders extend into the exhaust manifold 90 (FIGURE 2), and the exhaust ports of the other half of the cylinders extend into the exhaust manifold 92.

The use of two exhaust manifolds 90 and 92 intercoupled to alternate ones of the cylinders 48 is advantageous when the machine operates as a two-cycle combustion engine, as is the case With the illustrated embodiment.

With a single exhaust manifold there arises a difliculty in that exhaust gases from a given cylinder tend to impede the discharge of exhaust gases from the cyclically adjacent cylinders. This drawback is entirely eliminated in the engine disclosed herein, in which the cyclically adjacent cylinder exhaust ports are coupled to different exhaust manifolds.

The use of two exhaust manifolds is disclosed, for example, in the above-mentioned Patent No. 3,007,462, which, as mentioned, issued Nov. 7, 1961, to the present inventor.

The intake pistons 52 are each provided with a pocket, or depression, 94 at the inner end thereof. The fuel injector 70 is constructed so that it sprays fuel into the pocket 94 (FIGURES l and 1A).

The provision of the pocket 94, and of the injector 70 which directs the fuel spray into the pocket, prevents the washing of the cylinder bores with fuel and the resultant dilution of the lubricating oil.

Therefore, the combustion chamber of the engine of the present invention in each cylinder is bounded on one side by the fiat head of an exhaust piston so as to provide the most efiicient exhaust from the exhaust ports; and it is bounded on the other side by the pocketed head of an intake piston, which receives the injection spray from the fuel injector and prevents the spray from being washed out to the cylinder bore.

The fuel injector 70 is mounted in a positioning stud 98, and it extends through the stud. The stud 98 extends through the engine block 10, as shown in FIGURE 1, and it is threaded into the corresponding cylinder liner 82. The stud 98, therefore, additionally serves to hold the liner 82 against rotation. An O-ring seal 100 is mounted around the stud 98, as shown. As mentioned above, a separate fuel injector assembly is provided for each cylinder.

The fuel injector 70 is a dual spray type, and the tip of the fuel injector 70 is configured so that the fuel sprays issuing from the injector are inclined to the right at an angle of, for example, 18", as viewed in FIGURES 1 and 1C, and so directed into the pocket 94.

As viewed in FIGURE 1A, the dual fuel sprays extend at an angle, for example, of 34 on either side of the center line to completely cover the surface of the pocket 94. In this manner, all the fuel is directed into the pocket 94 and away from the face of the adjacent exhaust piston 50.

As mentioned above, the bore of each of the cylinder liners 82 is eccentrically positioned with respect to the bore of the corresponding cylinder. Appropriate grooves are formed in the outer surface of the liners which cooperate with mating grooves in the engine block to form the spaces 86 for the coolant; as well as spaces 88 for the intake manifold, and the spaces for the exhaust manifolds 90 and 92.

As mentioned, the O-ring seals are placed in circumferential grooves 84 in the eccentric rings which support the liner 82. This placement is more desirable than attempting to place the O-rings in inner peripheral grooves in the surface of the cylinder bore. The illustrated sealing construction enables a superior seal to be achieved between the liner and the corresponding cylinder bore; and also serves to facilitate the assembling of the different components. This construction also helps in the manufacture of the engine block 10 in that it eliminates the need for the formation of precise O-ring circumferential grooves around the inner surfaces of the cylinder bores.

Therefore, the cylinder liners 82 are supported in the cylinders 48 in the engine block 10 by integral annular eccentric rings which carry O-rings in their circumferential grooves 84. This allows for a closer connection between the pistons and the central shaft 12. It also provides greater clearance at the ports in their entrance to the adjacent manifolds.

The illustrated eccentric configuration of the cylinder liners 82 also permits the O-ring seals in the grooves 84 to be positioned away from the exhaust ports 54. This may be achieved by angularly positioning the exhaust port at locations where the O-rings are at their maximum radial displacement from the wall of the cylinder liner. This enables the seals to perform their sealing function with a relatively long lifetime because they are not subjected to intense corrosion and heat.

It will be noted from FIGURES 1 and 2 that the exhaust manifolds 90 and 92 are angularly positioned with respect to the corresponding cylinder liners to be where the eccentric relationship is the largest. This, as mentioned above, is where the O-ring seal is spaced furthest away from the exhaust port area, so as to be relatively remote from the intense heat and corroding action of the exhaust gases.

The bevel gears 76 and 80 are stationary gears, as mentioned, and they are mounted on opposite ends of the block 10. This mounting is achieved by bolts, such as the stud bolts 102 (FIGURES l and 1B). These gears also serve to retain the bearings 14 and 16 in the block 10, and they additionally serve to retain the cylinder liners against axial movement in their respective cylinders 48.

As best shown in FIGURE 3, the ball-ended connecting rods 62, which couple the pistons to the wabble spiders, extend into bearing sockets on the wabble spiders and in the respective pistons. That is, as shown in FIGURE 3, the ball and socket joint 64 includes a socket bearing portion 120, and the ball and socket joint 66 includes a socket bearing portion 122. These socket bearing portions 120 and 122 are interchangeable so as to simplify the construction of the machine.

Each of the socket bearing portions 120 and 122 include an inner bearing portion 124 and an annular split outer bearing portion 126 (FIGURE 4). The bearing portions 126 are split to permit access over the connecting rod 62.

A tubular clamping nut 128 threads into the wabble spider 60 to hold the

socket bearing portions

124 and 126 in place so as to trap the ball 64 in the corresponding ball and socket joint. The clamp nut 128 is provided with longitudinal slots 130 which are adapted to receive an appropriate tool for tightening the nut in place.

A tubular clamping nut 132 (FIGURE 5) threads into the end of the piston 50 to hold the

socket bearing portions

124 and 126 in place and trap the ball 66. The

clamping nut 132 is provided with slots 134 at its outer end which are adapted to receive an appropriate tool for tightening the nut 132 in place.

The clamping

nuts

128 and 132 have arcuate slots 138 formed in them. These slots impart an elasticity to the clamping nut so that they have a self-locking feature.

The invention provides, therefore, an improved reciprocating engine of the barrel type. The engine described herein has a central shaft and a plurality of parallel cylinders disposed at equi-angular positions about the shaft.

The reciprocating engine of the invention is constructed in an improved manner, as described above, for maximum efiiciency and so as to facilitate to a large extent the construction of the machine.

As mentioned, the cylinder liners of the machine of this invention are constructed to be offset with respect to the corresponding cylinder bores, and they are shaped to mount O-ring seals in an improved and simplified relationship. Also, the offset construction of the cylinder liners permits the associate pistons to be placed radially inwardly towards the central shaft to shorten the required connecting rod length, and provides for protection of the sealing O-rings by displacing them away from the hot gases from the exhaust ports.

The improved construction of the cylinder liners, as described above, permits the liners to cooperate with the engine block for the formation of manifold and cooling chambers.

In addition, the above-mentioned cylinder liners are held in place in a unique and improved manner by utilizing the bevel gears of the wabble spiders, and the liners are held against rotational motion by utilizing the fuel injectors.

Moreover, the important construction of the machine of the present invention also includes a flexible and versatile coupling for the connecting rods, as described above.

While a particular embodiment of the invention has been shown and described, modifications may be made, and it is intended in .the claims to cover all such modifications which fall within the spirit and scope of the invention.

What is claimed is:

1. In a barrel-type reciprocating machine which includes:

a block,

a shaft journaled in said block and including an oblique crank at at least one end thereof, said block having a plurality of cylinders formed therein parallel to the axis of rotation of said shaft and angularly spaced around said axis,

a wabble spider mounted on said oblique crank,

a plurality of pistons reciprocally mounted in corresponding ones of said cylinders,

and a plurality of connecting rods linking said pistons to said spider,

the combination of:

a sleeve member positioned in each of said cylinders said sleeve member extending within said cylinder throughout the length of the path of reciprocation of said piston therein and forming a closely-fitted housing for said piston, said piston reciprocally mounted in said sleeve member, said sleeve being insertable into said cylinder from one end of said cylinder,

end obstruction means extending from said block across at least a portion of each cylinder in a sleeve-blocking position,

and means for supporting and locking said sleeve member in an eccentric position in the corresponding ones of said cylinders.

2. The combination defined in claim 1 in which said supporting means comprises a plurality of eccentric annular members extending circumferentially around said sleeve member and spaced axially along the length of said sleeve member.

3. The combination defined in claim 1 in which said supporting means comprises a plurality of eccentric annular members extending circumferentially around said sleeve member and spaced axially along the length thereof, each of said annular members having a channel extending circumferentially around the periphery thereof, and O-ring sealing members positioned in respective ones of the circumferential channels in said eccentric annular members.

4. In a barrel-type reciprocating machine which includes:

a block,

a wabble spider mounted on said oblique crank,

and a plurality of connecting rods linking said pistons to said spider,

the combination of:

a sleeve member positioned in each of said cylinders and having ports formed therein,

and a plurality of eccentric annular members extending circumferentially around said sleeve member and spaced axially along the length thereof, said annular members defining manifold chambers within said block.

5. The combination defined in claim 4 in which said annular members are formed integral with said sleeve.

6. The combination defined in claim 4 in which said annular members each have a circumferential channel formed therein, and O-ring sealing members positioned in respective ones of the circumferential channels in said annular members.

7. In a barrel-type reciprocating machine which includes:

a block having an exhaust end and an inlet end,

a shaft journaled in said block and including an oblique crank at each end thereof, said block having a plurality of cylinders formed therein parallel to said shaft and angularly spaced around said shaft,

a pair of wabble spiders journaled one on each of said oblique cranks,

a plurality of pistons two in each of said cylinders and reciprocally mounted therein in opposed relationship,

a first plurality of connecting rods linking the pistons in the exhaust end of said block to one of said spiders,

and a second plurality of connecting rods linking the pistons in the intake end of said block to the other of said spiders,

the combination of:

a sleeve member position in each of said cylinders having exhaust ports formed therein at the exhaust end of said block and having intake ports formed therein at the intake end of said block, said ports being opened and closed by said pistons;

and means for supporting said sleeve member in an eccentric position in the corresponding one of said cylinders and defining coolant chambers at intake and exhaust manifolds with said block.

8.'The combination defined in claim 7 in which said supporting means com-prises a plurality of eccentric annular members extending circumferentially around said sleeve member and spaced axially along the length thereof, each of said annular members having a circumferential channel extending around the periphery thereof; and O-ring sealing members positioned in respective ones of the circumferential channels of said annular members.

9. In a barrel-type reciprocating machine which includes:

a block having a first end and a second end,

a pair of wabble spiders journaled one on each of said oblique cranks, a plurality of pistons two in each of said cylinders and reciprocally mounted therein in opposed relationship,

a first plurality of connecting rods linking the pistons in the first end of said block to one of said spiders,

and a second plurality of connecting rods linking the pistons in the second end of said block to the other of said spiders,

the combination of:

first and second bearings for said shaft positioned at opposite ends of said block;

sleeve members positioned in respective ones of said cylinders;

and bevel gear means for said spiders mounted on opposite ends of said block and serving to restrain said first and second bearings and said sleeve members from longitudinal movement relative to said block.

10. The combination defined in claim 9 and which includes fuel injector means extending radially into each of said cylinders through corresponding ones of said sleeve members and which restrains said sleeve members against angular movement relative to said block.

11. The combination defined in claim 1 and which includes a counterweight mounted on said shaft and having a notch formed therein to facilitate the removal of said connecting rods.

References Cited by the Examiner UNITED STATES PATENTS 1,042,018 10/12 Macomber 12358 1,116,768 11/14 Underwood 7414 1,476,275 12/23 Wishon 12358 1,716,020 6/29 Winckler 9270 1,978,194 10/34 Gray 123--58 2,110,116 3/38 Alfaro 123-32 2,132,083 10/38 Pescara 123-32 2,440,310 4/48 Thege 123-51 3,007,462 11/61 Balzer 123-58 FRED E. ENGELTHALER, Primary Examiner.

Claims

7. IN A BARREL-TYPE RECIPROCATING MACHINE WHICH INCLUDES; A BLOCK HAVING AN EXHAUST END AND AN INLET END, A SHAFT JOURNALED IN SAID BLOCK AND INCLUDING AN OBLIQUE CRANK AT EACH END THEREOF, SAID BLOCK HAVING A PLURALITY OF CYLINDERS FORMED THEREIN PARALLEL TO SAID SHAFT AND ANGULARLY SPACED AROUND SAID SHAFT, A PAIR OF WABBLE SPIDERS JOURNALED ONE ON EACH OF SAID OBLIQUE CRANKS, A PLURALITY OF PISTOSN TWO IN EACH OF SAID CYLINDERS AND RECIPROCALLY MOUNTED THEREIN IN OPPOSED RELATIONSHIP, A FIRST PLURALITY OF CONNECTING RODS LINKING THE PISTONS IN THE EXHAUST END OF SAID BLOCK TO ONE OF SAID SPIDERS, AND A SECOND PLURALITY OF CONNECTING RODS LINKING THE