US3270685A

US3270685A - Rotary radial piston machine

Info

Publication number: US3270685A
Application number: US292629A
Authority: US
Inventors: Eickmann Karl
Original assignee: Individual
Current assignee: Individual
Priority date: 1962-07-04
Filing date: 1963-07-03
Publication date: 1966-09-06
Anticipated expiration: 1983-09-06
Also published as: DE1453435A1; DE1453435C3; DE1453435B2

Description

Sept. 6, 1966 K. EICKMANN 3,270,685

ROTARY RADIAL PISTON MACHINE Filed July 5. 1963 12 Sheets-Sheet 1 R 7 5 1 it 1 I INVENTOR.

k w, w k k m KARL E/C/(MANN BY afl M Sept. 6, 1966 K. ElCKMANN ROTARY RADIAL PISTON MACHINE l2 Sheets-5heet 2 Filed July 5, 1965 r mm INVENTOR. KARL E/C/(MAN/V BY 7 1% M 7M Arwm/z s Sept. 6, 1966 K. EICKMANN 3,270,685

ROTARY RADIALPISTON MACHINE Filed July 5, 1963 12 Sheets-Sheet 3 INVENTOR. KARL E/CKMfi/VN P 5, 1966 K. EICKMANN ROTARY RADIAL PISTON MACHINE l2 Sheets-Shea t 4 Filed July 5. 1963 mvEN'roR. KARL E/CKMA/VA/ W411 AMX/ 7M1) Sept. 6, 1966 K. EICKMANN ROTARY RADIAL PISTON MACHINE 12 Sheets-Sheet 5 Filed July 5. 1963 INVENTOR. KARL E/C/("ANN BY 7 W M 1/ 7:14

Sept. 6, 1966 K. EICKMANN 3,270,685

ROTARY RADIAL PISTON MACHINE Filed July 5, 1965 12 SheetsSheet e JNVENTOR.

KARL EICKMAN/V BY 714 3120] ML 76 Sept. 6, 1966 K. EICKMANN 3,

ROTARY RADIAL PISTON MACHINE Filed July 5. 1963 12 Sheets-Sheet 7 INVENTOR. I64 R1. E/GKMANN BY hwewWL/iw Sept. 6, 1966 K. EICKMANN ROTARY RADIAL PISTON MACHINE E Q a .+b 5 C 0 y a I. m R, S m 2 r 1 n Y B Q QQExb-u QQU A 101 Jf/S Sept. 6, 1966 K. EICKMANN ROTARY RADIAL PISTUN MACHINE 12 Sheets-Sheet 9 Filed July 3. 1963 INVENTOR. KARL E/C/(MA/WV BY 7K1) M M l2 Sheets-Sheet 10 Filed July 3. 1963 kWN MDN

JNVENTOR. KARI. E/C/(IVMN/V 12 Sheets-Sheet 11 Filed July 5. 1963 Wm mt kWh INVENTOR- KARL E/CKMANN Sept. 6, 1966 K. EICKMANN ROTARY RADIAL PISTON MACHINE l2 Sheets-Sheet 12 Filed July 3. 1963 ll! 8 A/////// Q Q INVENTOR.

KARL E/CKMAN/V BY 71H: ,m,

A rrozw s NW 9k United States Patent Ofi ice 3,270,685 Patented Sept. 6, 1966 15 Claims. to. 103161) This invention relates to rotary radial piston machines and, more particularly, to a rotary radial piston machine having plural groups of cylinders with each group including plural cylinders, the axes of the cylinders of each group lying in a common plane which is perpendicular to the axis of the rotor of the machine, and the respective groups of cylinders being spaced axially from each other. The machine is intended to operate with fluid such as liquid or gases in the cylinders, and may be used in the form of a variable or constant compressor, pump, hydraulic motor, rotary combustion engine or the like in which the piston strokes, during rotation, have either a constant or a variable length.

Such rotary radial piston machines are known, and include a plurality of substantially radial cylinders formed in a rotor. Pistons are recipro-cable in these cylinders during operation of the machine under power, to increase and decrease the cylinder volumes inwardly of the inner ends of the pistons. Machines of this type have been very useful in operation and in practical applications. However, it is still possible to increase the power output as well as the total efficiency of such machines.

An object of the present invention is to provide a rotary radial piston machine having an increased power ouput and an increased overall efiiciency.

A further object of this invention is to provide a rotary radial piston machine including groups of cylinders each including plural cylinders arranged in a machine which has a relatively small overall size and weight in comparison to its possible power output.

In prior art variable output pumps or motors, it was not realized how important it is that such machines be of small size, small weight, and simple in construction and operation while providing high power and high efficiency. Furthermore, insufiicient attention was paid to the fact that the liquid fiows must be accurately sealed from each other so that they cannot have adverse influences on each other resulting in failures of the machines to perform properly. Furthermore, the relatively large dimensions of prior art machines results in relatively elongated paths of movement between parts with corresponding increased friction, and the low pressure of such machine results in the high percentage of losses in output power.

A further object of the invention is to provide a rotary fluid machine including plural cylinder groups each including plural cylinders, and which is compact and small in dimension compared with its power output whereby to lower its cost, to increase its etliciency and to increase its useful life.

Yet another object of the invention is to provide a rotary fluid machine of the type just mentioned in which the increase in power output, efficiency and useful life is effected by shortening the paths of relative movement of adjacent parts, by balancing forces, by floating mounting of parts, and by stabilization of the guiding of parts.

In accordance with the invention, there are at least two groups of cylinders provided in the rotor. The axes of all of the cylinders of any one group lie in a common diametric plane through the rotor. The diametric planes of the several cylinders groups are spaced axially from each other. Consequently, by providing the plural cylinder groups, it is possible to multiply the power output of the machine compared to one of the same dimensions but having only a single cylinder group. This results in a decrease of friction relative to the power output and coresponding increase in the efficiency.

Yet another object of the invention is to provide a rotary fluid machine of the type mentioned in which radial forces acting on the rotor are balanced by dividing the cylinder-pistons into two groups with the pistons in one group always moving in the reverse direction with respect to the pistons in the other group, the two groups being equal in number of cylinder-pistons.

A further object of the invention is to provide an arrangement whereby each cylinder group can have a separated flow, plural cylinder groups can have separated flows, plural cylinder groups can cooperate for a provision of the combined flow, each piston group can be driven by a separated flow, plural piston groups can be driven by plural separate flows, and plural piston groups can be driven by a combined flow.

In accordance with a further object of the invention, a plurality of control ports are provided in a control body for cooperation with the rotor and with passages leading to the cylinders in the rotor or rotors.

In accordance with another object of the invention, each guide means of the machine has at least three surfaces for guiding the pistons or the piston guide shoe assembly during radial reciprocation, and in which the pistons or the piston guide shoes are guided radially inwardly by at least one guide surface of the machine.

In accordance with the invention, it is possible to substantially eliminate friction on pistons and piston guide shoes and also to prevent heating, sticking or welding of pistons, piston guide shoes and their adjacent or guiding parts. It is further possible to obtain long piston strokes and thereby to increase the flow quantity through the machine, to balance radial forces acting on the rotor or rotors and on the pistons or the piston guide shoes, to provide a plurality of cylinder groups in the machine, to provide a plurality of separate fluid flow passages in the machine, and to increase considerably the power and efficiency of this type of machine.

For an understanding of the principles of the invention, reference is made to the following description of typical embodiments thereof as illustrated in the accompanying drawings.

In the drawings:

FIG. 1 is an elevation view of a piston guide shoe such as used in the embodiment of the invention shown in FIG. 16.

FIG. 2 is a sectional view taken along line IIII of FIG. 1;

FIG. 3 is a plan view of the guide shoe shown in FIG. 1;

FIG. 4 is an axial sectional view through one form of rotor embodying the invention;

FIG. 5 is a sectional view taken along the line VV of FIG. 4;

FIG. 6 is an axial sectional view through another form of rotor embodying the invention and taken along the line VI-VI of FIG. 7.

FIG. 7 is a diametric sectional view through the rotor of FIG. 6 and taken along the line VII-VII of FIG. 6;

FIG. 8 is an axial sectional view through one form of guide ring embodying the invention;

FIG. 9 is an elevation view of the guide ring shown in FIG. 8 looking in the direction of the arrow VIII-VIII;

FIG. 10 is an axial sectional view through another form of guide ring embodying the invention;

FIG. 11 is an elevation view of the guide ring shown in FIG. 10, looking in the direction of the arrow XIXI;

FIG. 12 is an axial sectional view through a further form of guide ring embodying the invention;

FIG. 13 is a diamelrical sectional view through the guide ring shown in FIG. 12 taken along the line XIII XIII of FIG. 12:

FIG. I4 is a diametric sectional view through still another form of guide ring embodying the invention and taken along the line XIVXIV of FIG. 15;

FIG. 15 is an elevation view of the guide ring shown in FIG. I4 looking in the direction of the arrow XV-XV;

FIG. 16 is an axial sectional view through a multi-cylinder group rotary fluid machine embodying the invention;

FIG. 17 is an axial sectional view through another embodiment of rotary fluid machine in accordance with the invention;

FIG. 18 is an axial sectional view through still another embodiment of rotary fiuid machine in accordance with the invention;

FIG. 19 is a longitudinal sectional view through still another multi-fluid rotary machine embodying the invention; and

FIGS. 20, 2t and 22 are diagrammatic sectional views through FIG. 18 taken along the lines XXXX, XXI XXI and XXIIXXII, respectively.

As stated, the present invention is directed to a rotary fluid machine in which there are a plurality of cylinder groups with each group including a plurality of cylinders. Each cylinder has a piston associated therewith for reciprocation therein. In accordance with the present inven tion, the axes of the cylinders of each group lie in a common diametric plane through the rotor or rotors of the machine, and these planes are spaced axially from each other. In order to show this important feature of the invention, the several planes are shown by section lines such as the section lines 32 and 33 of FIG. 16, 132 and 133 of FIG. 17, 232, 233 and 332, 333 of FIG. 18, and 432, 433 and 532, 533 of FIG. 19.

The pistons 11 reciprocating in the respective cylinders are provided with pivoted piston guide shoes. Referring to FIGS. 1, 2 and 3, a preferred embodiment of the piston guide shoes is shown as being similar to those of my allowed copending patent application Serial No. 229,644. As illustrated, each piston 1 has a trunnion portion 2 and a central part 4 which is integral with trunnion 2 and extends radially therefrom. The trunnion 2 is arranged to be oscillatably received in the usual slot provided in a bore of the piston, such as the piston 11 of FIG. 7, so that the guide shoes can oscillate about axes which are parallel to the rotor axis.

Center part 4 of each guide shoe is provided, at each end, with circumferentially extending or arcuate extension members 3 integral therewith. These extensions have radially outer guide surfaces 5, radially inner guide surfaces 6, and radially extending end guide surfaces 7. The several guide surfaces cooperate with respective guide surfaces of stationary or rotary guide members. Referring to FIG. 4, the dual or twin rotor 8 is provided with two diametric planes, each having a group of cylinders associated therewith, these planes being indicated at 32 and 33. The axes of all the cylinders of one group are located in the plane 32, and the axes of all the cylinders of the second group are located in the plane 33. Rotor 8 further has two annular ribs 34 extending radially outwardly therefrom, each of these ribs being centered axially on a

respective plane

32 or 33. Between ribs 34, the rotor outer diameter is reduced by virtue of the annular recess 35 in the outer surface of the rotor.

The piston guide shoes as illustrated in my mentioned allowed copending patent application Serial No. 229,644 are particularly suitable for use in the present invention since they are simple in design, stably transmit traction and pushing forces in a substantial radial direction, and make possible long piston strokes. Consequently, this form of guide shoe is illustrated in the several embodiments of the invention.

Again referring to FIGS. 4 and 5, rotor 8 may have a rotor hub or axial bore 13, and it will be noted that FIG. is a sectional view taken along the diametric plane 33 of FIG. 4. A feature of the embodiment of the rotor shown in FIGS. 4 and 5 is that the cylinders and 11 of the respective groups are aligned with each other in a direction axially of the rotor. Each cylinder communicates with the rotor bore 13 through a port and passage 14, and the bore forming each cylinder is drilled through the corresponding rotor rib 34 so as to provide slots 9 in these ribs.

FIGS. 6 and 7 show another embodiment of a twin rotor indicated at 15. This rotor is likewise provided with two groups of cylinders, one group having the cylinder axes lying in the diametric plane 133 and the other group having the cylinder axes lying in the diametric plane 132. Thus, the axes of cylinder 16 lie in plane 133 and the axes of cylinder 17 lie in plane 132 which is spaced axially from plane 133. As in the embodiment of FIGS. 4 and 5, each cylinder is provided with an axially extending slot 9 through the associated annular rib 52, there being two of these annular ribs on rotor 15. As the bores forming the cylinders are formed through annular ribs, the slots 9 result providing the spaced wall portions having the arcuate inner surfaces 53 congruent with the inner surfaces of these cylinders.

The feature of the embodiment of rotor shown in FIGS. 6 and 7 is that the axes of cylinders 16 are angularly offset with respect to the axes of cylinders 17, with the axes of cylinders 16 lying angularly substantially midway between the axes of cylinders 17. Between the several cylinders, the exterior surface of rotor may be recessed as indicated at 18 to reduce the weight of the rotor or to provide space for parts cooperating with the rotor and the cylinders and pistons. Rotor 15 may be characterized as an angularly spaced twin rotor. FIG. 7 also shows a piston 11 and its guide shoe 1 mounted in one cylinder. Furthermore, an annular recess 55 may be provided in the outer surface of rotor 15 between the two sets of cylinders, this annular recess lying between the relatively narrow extensions 52.

Referring to FIGS. 8 and 9, a stroke ring 19 is shown which is mounted between two piston groups of the twin rotors. A feature of ring 19 is that it can enter into the radially outer recess of the rotor 35 of rotor 8 shown in FIGS. 4 and 5 or the radially outer recess 55 of the rotor 15 shown in FIGS. 6 and 7. However, the stroke ring 19 of FIGS. 8 and 9 is particularly suitable for cooperation with the twin rotor 8 of FIGS. 4 and 5. Ring 19 has an annular radially outwardly extending rib or extension 22 whose outer surface forms a stroke ring seat 23 and whose side surfaces form radially extending guide surfaces 21 and 24. Axially extending guide surfaces and 25 are provided on the outer surface of ring 19 on either side of the rib 22. The junction of

surfaces

20 and 21 and the junction of

surfaces

24 and 25, may be relieved as indicated.

Another form of stroke ring is illustrated at 27 in FIGS. 10 and 11. This is a twin stroke ring and therefore is provided with a pair of radially outwardly extending and circumferentially interrupted

flanges

36 and 39, one at each end of ring 27. The radially outer surface of ring 27 between the

flanges

36 and 39 provides a groove 31, which is generally channel-shaped. Stroke ring seats 27 and are provided by the radial outer surfaces of the

flanges

36 and 39, and gaps or recesses 18 are provided in the flange 36 and gaps or recesses 118 are provided in the flange 39.

The twin stroke ring shown in FIGS. 10 and 11 is particularly suitable for use in twin rotors wherein the diametric planes including the cylinder axes are relatively close to each other. The form of the ring shown in FIGS. 10 and 11 provides radially extending guide surfaces 28 and 29 and an axially extending guide surface 20.

FIGS. I2 and 13 show another embodiment of the twin stroke ring provided with a groove 31, ring seats 27 and 30, and

flanges

36 and 39. Notches 37 extend inwardly from one axial end edge of the ring, and notches 38 extend inwardly from the other axial end edge, the notches 37 being angularly staggered with respect to the notches 38. Radial guide surfaces 28 and 29 are provided on the flanges, while the guide member also includes an axially extending guide surface 20. The twin ring of FIGS. 12 and 13 is particularly suitable for use with the twin rotors of the type shown in FIGS. 6 and 7 and can enter into the radially outer recess 55 or into the recesses 18.

The twin stroke ring shown in FIGS. 14 and has a design essentially similar to that of the ring shown in FIGS. 12 and 13 but differs therefrom in that the

flanges

39 and 41 have a much smaller axial spacing from each other than do the

flanges

39 and 36 of FIG. 12. This embodiment of the twin ring is particularly suitable for twin rotors wherein the diametric planes including the axes of the cylinder groups are closely adjacent each other axially of the rotor. The

parts

40, 56, 20, 44, 45, 48 and 49 of the ring shown in FIGS. 14 and 15 are similar to the corresponding

parts

27, 30, 20, 28, 29, 38 and 37 of the ring shown in FIGS. 12 and 13. The junctions of the axially and radially extending guide surfaces may be relieved as indicated at 43.

FIG. 16 shows a rotary fiuid machine utilizing the rotor 8 of FIGS. 4 and 5 and having the

diametric planes

32 and 33 containing the axes of their respective cylinder groups. The stroke ring 22 shown in FIGS. 8 and 9 is mounted between the two sets of piston guide shoes. The radially extending guide surfaces 7 of. the piston guide shoes 1 have guiding engagement with the radially extending guide surfaces 21 or 24 of stroke ring 22, and also with the radially extending guide face 42 of a support ring 54. A feature of this embodiment of the invention is that a rotatable ring 55 extends axially between the two support rings 54 and is carried by these two support rings thereby providing the axially extending radially inner guide face 56 which is in bearing engagement with stroke ring 22 and which has guiding engagement with the radially outer guide surfaces 5 of the piston guide shoes of the two groups. The radially inner guide surfaces 6 of the piston guide shoes having guiding engagement with axially extending guide surface 57 on support rings 54 and with the axially extending guide surfaces and of stroke ring 22. Stroke ring 22 can enter recess between the ribs 34 of twin motor 8.

The machine shown in FIG. 16 has an outer casing 62 including a closure 68 which fixedly supports a pintle 69. Rotor 8 is rotatable on a bushing 58 on pintle 69, and is retained against axial displacement by retaining means 61. A shaft 63 may be connected to rotor 8 by clutch or coupling means 64 and is rotatable in a bearing 65. Support rings 54 rotate on bearings 66 which may be adjusted by an adjusting device 67 to control the relative eccentricity of the guide means with respect to the rotor axis.

Pintle 69, or rather its support wall 68, is formed with connection ports 70 through which fluid flows to pintle passages 59 and 60. Ports 14A and 14C connect passages 5-9 and 60, respectively, to cylinders 10 through ports 14. Similarly, ports 14B and 14D connect passages 59 and 60, respectively, to cylinders 10 through passages 14.

FIG. 17 shows another embodiment of rotary fluid machine in accordance with the invention. In this embodiment, a stationary pintle 169 is also formed with passages 159 and 160 and with respective twin control ports 114C, 114D, 114A and 114B. However, these ports are axially much closer together than the corresponding ports in the embodiment of FIG. 16. The rotary support rings 54 of FIG. 17 are generally similar to support rings 54 of FIG. 16, and the rotatable ring is generally similar to the ring 5 5 of FIG. 16. A feature of the embodiment of the invention shown in FIG. 17 is that the twin rotor 15 of FIGS. 6 and 7 is used. Additionally, FIG. 17 illustrates how the twin stroke ring 39' of FIGS. 14 and 15 is used. The two planes containing the axes of the respective cylinder groups are shown at 132 and 133. The eccentricity adjusting device 67 acts in a manner disclosed in other variable rotor machines shown in my patent applications and patents. The machine includes a casing 162 having an enclosure wall which is an integral extension of the pintle 169. The other parts are similar to those shown in FIG. 16.

The embodiment of the invention shown in FIG. 17 has two special features. The first feature is that, by virme of the angularly spaced twin rotor" 15, the angular spacings between two circumfcrentially adjacent cylinders are relatively small and consequently the operation of the machine is relatively silent with only relatively small vibrations and load changes. The second feature is that, using the rotor 15, fluid machines may be built which are relatively short in an axial direction.

FIG. 18 illustrates a multi-tlow rotary fluid operated or fluid operating machine in accordance with another embodiment of this invention. In this embodiment of the invention, there are eight pintle passages 112 through 119 formed in the control pintle 136 and each associated with a respective control port 120 through 127. The pintle 136 also has

connection ports

131, 130, 129, 128, 132, 133, 134 and 135 each associated with a respective passage. Thus, pintle passage 112 interconnects control port 120 and connection port 128, pintle passage 113' interconnects control port 121 and connection port 129, pintle passage 114 interconnects control port 122 and connection port 130, passage 115 interconnects control port 125 and connection port 131, passage 116 interconnects control port 127 and connection port 132, passage 117 interconnects control port 126 and connection port 154, and passage 119 interconnects control port 124 and connection port 135.

All of the pintle passages extend through control pintle 136- and pass fluid in either direction relative to the respective cylinders. The pintle passages are sealed from each other and any communication between the same is prevented. The connection ports are provided for connection of pipes or tubes, and it will be noted that these ports are arranged in one

group

128, 129, 130 and 131 and a

second group

132, 133, 134 and 135. During operation of the machine, one group of connection ports serves for flow of fluid into the machine while the other group of connection ports serves for exhaustiv fluid from the machine. It will therefore be understood that the machine has four fluid inlets and four fluid outlets. Machines of the type shown in FIG. 18 are therefore able to drive machines, such as vehicles, which have at least four working places or fluid motors, and prevents slip or free running between the different motors.

The pistons in FIG. 18 have their axes in four different diametric planes which are spaced axially from each other. The control ports and 124 are associated with the group of cylinders having axes in the plane 232. These two control ports are in diametric opposition, so that one acts as a supply port and the other acts as an exhaust port.

Control ports 1'21 and are operatively associated with the cylinders having axes in plane 233. These ports also are diametrically opposite each other, with one serving as an inlet port and the other serving as an exhaust port for the associated cylinders. Control ports 122 and 126, which are also in diametrically opposite relation, cooperate with those cylinders which have their axes in the plane 333, with one control port acting as an inlet port and the other acting as an outlet port. Control ports 125 and 127 are operatively associated with those cylinders having their axes lying in the plane 232. These ports, which are diametrically opposite each other, act as inlet and outlet ports, respectively, for the associated cylinders.

The machine shown in FIG. 18 includes cylinders 110 having their axes in plane 232, cylinders 112 having their axes in plane 233, cylinders 212 having their axes in plane 333, and cylinders 210 having their axes in plane 332. In this embodiment of the invention, there are two

eccentricity adjustment devices

167 and 267 which may slide on guide segments 567 as illustrated more fully in 7 FIG. 20. Part 267 is the inner adjustment device while part 167 is the outer adjustment device. An adjustment bolt 84 is provided and has oppositely directed

threads

72 and 73. Consequently, adjustment of bolt 84 results in movement of

adjustment devices

267 and 167 either toward each other or away from each other. If both adjustment devices are in the zero position, the stroke of the pistons is zero. However, if the adjustment devices are spaced widely from each other, delivery is a maximum because the piston strokes are a maximum. If the two adjustment devices are at their minimum spacing, the flow of fluid through the machine is reversed and reaches a maximum because the piston stroke is also a maximum.

Those pistons having their axes in

planes

232 and 332 move radially in unison with each other, while those pistons which have their axes in planes 233 and 333 move in unison but in opposition to the pistons, having their axes in

planes

232 and 332. Thus, if the pistons in

planes

232 and 332 are moving radially outwardly, then the pistons in

planes

233 and 332 are moving radially inwardly, and vice versa. Thus, the fluid forces acting on all of the cylinders against control pintle 136 are entirely in balance it all the pistons have the same diameter and if each group of pistons includes the same number of cylinders.

The embodiment of the invention shown in FIG. 18 also provides the very important feature of total balancing of the rotor and or the control pintle, which provides for high pressure operation with high power output and with a high efiiciency. Two twin rotors 8 may be used in the machine and may be rotatably mounted on a bush ing 158, the rotors being fixed in position by a distance ring 258 and retaining means 61. Stroke rings 119 may be provided, each cooperating with all of the piston guide shoes associated with pistons having axes in the same diametric plane. Guide member ring 71 may be provided to guide the stroke rings 119, the respective rotatable rings 154 and the respective support rings 254. The support rings 154 and 254 are characterized in that they are supported at one end only in

bearings

66 and 166. The opposite ends bear against the respective guide rings 71. This arrangement saves space in an axial direction. Support rings 154 and 254 may be integral with

rotating rings

155 and 255 and secured in position 'by rotating rings 161. The closure 168 for the casing 162 may be integral with the pintle 163. A front cover 74 and the back closure 168 are fastened in casing 172 by retaining rings or snap rings '75. The adjustment means, or more particularly the outer adjusting device 167, acts as a distance piece between front cover 74 and back cover 168 which eliminates the necessity for further securing or fastening bolts and also saves space.

Other parts of the embodiment of the invention shown in FIG. 18 may act in a manner similar to other embodiments of the invention or as in the prior art, and it is therefore assumed that those skilled in the art will understand their locations, functions and actions and that a further detailed description is not necessary. The sections shown in FIGS. 20, 21 and 22 clearly illustrate the construction of the embodiment of the invention shown in FIG. 18. FIG. 21 illustrates another embodiment of the rotor.

Referring to the embodiment of the invention shown in FIG. 19, this is another entirely balanced rotary fluid machine. In this embodiment, there is only one inlet and one outlet flow and therefore only two

connection ports

165 and 166 are necessary. A pintle passage 173 interconnects control

ports

169, 166, 167 and 172 with connection port 165, and a pintle passage 174 interconnects control

ports

165, 170, 168, and 171 with connection port 166.

Control ports

165, 166, 167 and 168 are visible in FIG. 19. Control ports 169 through 172 are not visible because they are located in the diametrically opposite half of the pintle but in similar locations. Those pistons whose axes lie in the

planes

432 and 532 are moving radially inwardly at the same time that those pistons whose axes lie in the

planes

433 and 533 are moving radially outwardly. The adjustment of the piston strokes and the adjustment of reversibility of flow is similar to that of the embodiment of FIG. 18.

A feature of the embodiment of FIG. 19 is the provision of a larger number of hearings in order to provide stability for each rotating ring or each guide member. The piston guide shoes of pistons having their axes in

planes

432 and 532 have guided cooperation with rotatable rings 255 and support rings 254. The piston guiding shoes of those pistons having their axes lying in the

planes

433 and 533 have guided cooperation with the respective support ring 354, a rotatable ring 355 and stroke ring 271. Since the pressure of fluid in those cylinders having their axes in

planes

432 or 532 acts in opposition to the pressure of fluid in those cylinders having their axes in

planes

433 or 533, the rotor or rotors float on control pintle 269.

Bearings 66 are mounted in the outer eccentricity adjusting device 467 to rotatably mount rotary support rings 254 which carry the rotatable rings 255.

Rings

255 and 254 may be fitted against each other, carried by each other, or secured together by interfitting parts, such as grooves and ribs, or by retaining means such as retaining rings. Support rings 254 and rotatable rings 255 guide the reciprocation of the pistons in cylinders having their axes in

planes

432 and 532. The rings and their bearings 66 are located at adjacent opposite axial ends of the outer guide member or eccentricity adjusting device 467.

Inboard bearings 266 are located inwardly of the outboard bearings 66 and mounted in the inner eccentricity adjusting device 367. Bearings 266 support rings 354 which further support ring 355. Guide rings 371 are located between each inboard bearing 266 and the adjacent outboard bearing 66. Support rings 354 with rotatable rings 355 guide the reciprocations of those pistons operating in the cylinders having their axes located in the

planes

433 and 533.

A twin rotor 15 is mounted on a bushing 458 substantially in the center of the latter, and adjacent each end of twin rotor 15 there is a single rotor 108 and 209 also mounted on the bushing 458. Control pintle 269 either may be mounted in back cover 268, may be integral therewith, or may be secured in casing 162. This pintle 269 may also be a floating control pintle such as shown in my British Patents 909,088 and 909,089.

The provision of the outer and inner adjustment devices 367 and 467 of the embodiment of FIG. 19 provides an especially stable structure as a result of the planes of the cylinder axes being evenly spaced axially to either side of the longitudinal center line of adjustment bolt 84. Due to the balanced pressures, the rotors and the pintle float relative to each other where-by the machine may have a high power and a high efliciency such as in the embodiment of FIG. 18 provided the pistons and cylinders are properly dimensioned and located.

The remaining components of the machine of FIG. 19 may be similar to those in the other embodiments of the invention, may have functions similar thereto, or may be components known from the prior art, and it is assumed that those skilled in the art can understand the locations, principles and functions so that further detailed description does not appear necessary. Fluid pressure balancing recesses 78 can be provided in the outer surfaces of piston guide shoes 1, and may further be provided on the control means or control panel or on the rotor or rotors.

It should be understood that insofar as there are disclosed control pintles extending into respective rotor hubs, this by way of example only. Instead of the illustrated control means, control means or control bodies provided with plane, conical or spherical control faces, and which slide on the axial end faces of a rotor or rotors can be provided and suitably formed for control of the flow of fluid. The details of the different embodiments of the invention may be used separately or in combination,

and detailed features of one embodiment may be also used in another embodiment. Furthermore, the fluid operated for operating rotary machines can operate, or can be operated, either by liquid or gas. It should further be understood that the term fluid as used herein means either a liquid of a gas or something which has the ability to flow.

While specific embodiments of the invention have been shown as described in detail to illustrate the application of the principles of the invention, it will be understood that the invention may be embodied otherwise without departing from such principles.

What I claim is:

1. A rotary fluid machine comprising, in combination, a casing; at least one rotor rotatably mounted in said casing and formed with angularly spaced radial bores constituting cylinders; pistons reciprocable in each of said cylinders to vary the effective volumes of the cylinders to displace fluid relative to said cylinders; guide means surrounding said rotor and reciprocating said pistons upon rotation of said rotor; said guide means having an eccentricity relative to the rotor axis to define the piston strokes; said cylinders being arranged in at least two groups with the cylinders of each group having their axes in a respective common diametric plane through said rotor, said planes being spaced axially of said rotor; said rotor having at least two external annular radial ribs each centered axially on a respective one of said diametric planes, the axial widths of said ribs being less than the diameter of the associated bores; said guide means being formed to provide radially inwardly opening annular grooves arranged to have said ribs extend at least partially thereinto; said bores being formed through said ribs to provide extended guide surfaces for said pistons, with resultant axial slotting of said ribs at angularly spaced locations each centered on a respective cylinder axis; the cylindrical surface of said rotor being formed, between axially adjacent ribs, to have said guide means move at least partially close to it; whereby the effective piston stroke is increased substantially relative to the rotor diameter; and fluid inlet and outlet means communicating with said bores.

2. A rotary fluid machine comprising, in combination, a casing; at least one rotor rotatably mounted in said casing and formed with angularly spaced radial bores constituting cylinders; pistons reciprocable in each of said cylinders to vary the effective volume of the cylinders to displace fluid relative to said cylinders; guide means surrounding said rotor and reciprocating said pistons upon rotation of said rotor; said guide means having an eccentricity relative to the rotor axis to define the piston strokes; said cylinders being arranged in four groups with the cylinders of each group having their axes in a respective common diametric plane through said rotor, said planes being spaced axially of said rotor; said diametric planes being arranged in pairs spaced axially in balanced relation relative to a central diametric plane through said rotor; the pistons in the two axially innermost groups moving radially outwardly in their respective cylinders as the pistons in the two axially outermost groups move radially inwardly in their respective cylinders.

3. A rotary fluid machine, as claimed in claim 2, including guide shoes each operatively connected to a respective piston; said guide means comprising a first cylindrical guide means operatively engaged with the guide shoes connected to the pistons reciprocating in the axially innermost pair of groups, and a second cylindrical guide means operatively engaged with the guide shoes connected to the pistons of the axially outermost pair of groups.

4. A rotary fluid machine, as claimed in claim 2, in which said guide means comprises a first cylindrical guide means for reciprocating the pistons of the axially innermost pair of groups, and a second cylindrical guide means for reciprocating the pistons of the axially outermost pair of groups; and means for conjointly adjusting the respective eccentricities of said first and second cylindrical guide means in opposite directions.

5. A rotary fluid machine, as claimed in claim 2, said rotor being rotatably supported on a pintle non-rotatably mounted in said casing; said pintle being formed with radial port means each communicating with the bores located in a respective diametric plane, and being formed with plural connection ports in an axially outer end thereof and equal in number to said radial port means; said pintle being further formed with plural axially extending passages each connecting a respective connection port to a respective radial port means.

6. A rotary fluid machine, as claimed in claim 5, including a bushing interposed between said pintle and said rotor and formed with radial ports each registrable with the radial port means in a respective diametric plane.

7. A rotary fluid machine, as claimed in claim 2, in which there are four groups of cylinders, there being two groups on either side of the central diametric plane through said rotor, the four groups being arranged in balanced relation with respect to said central diametric plane; each radial port means comprising a pair of diametrically opposite radial ports, and there being eight of said connection ports arranged in two groups of four each; one group of four connection ports being connected to those radial ports on one side of an axial plane through said pintle, and the other group of four connection ports being connected to those radial ports on the opposite side of said axial plane through said pintle; one of said groups of connection ports being inlet ports and the other of said groups of connection ports being outlet ports.

8. A rotary fluid machine, as claimed in claim 7, in which the pistons in the two axially inner groups of cylinders move simultaneously radially inwardly while the pistons in the two axially outer groups of cylinders move simultaneously radially outwardly whereby the radial forces on said rotors and said pintle are balanced.

9. A rotary fluid machine, as claimed in claim 1, including guide shoes each operatively connected to a re spective piston; each of said piston guide shoes including a connection portion pivotally connected to the associated piston for pivoting of the guide shoe about an axis parallel to the axis of said rotor, said connection portion having dimensions such as to fit within the associated cylinder, a mounting portion extending outwardly from said connection portion, a bar extending from said mounting portion axially in both directions substantially parallel to the rotor axis and having a width such as to be able to enter within the axially extending slots of said ribs, and a pair of circumfercntially extending arcuate shoe portions each at a respective end of said bar.

10. A rotary fluid machine, as claimed in claim 9, in which said rotor is formed with recess means comprising a radially inwardly extending recess extending annularly of the cylindrical surface of said rotor; said guide means including a ring having a portion extendable at least partially into said annular recess; said ring having a pair of radially outer axially spaced guide surfaces engageable with radially inner arcuate surfaces of the guide shoes of pistons in axially adjacent groups of cylinders; said ring including a substantially rectangular rib extending radially outwardly between said guide surfaces and having radial guide surfaces engageable with the radially extending side edges of the guide shoes of the pistons of axially adjacent groups of cylinders.

11. A rotary fluid machine, as claimed in claim 8, in which said rotor has an external annular radial rib centered axially of each diametric plane, the axial widths of said ribs being less than the diameter of the associated bores; said guide means being formed to provide radially inwardly opening annular grooves arranged to have said ribs extend at least partially thereinto; said bores being formed through said ribs to provide extended guide surfaces for said pistons, with resultant axial slotting of said ribs at angularly spaced locations each centered on a respective cylinder axis; and in which there are four rotors including a twin rotor having a pair of said annular ribs and having the cylinders of the two axially inner groups arranged therein, and a pair of rotors each axially adjacent a respective opposite end of said twin rotor and each having formed therein the cylinders of a respective one of said axially outer groups of cylinders.

12. A rotary fluid machine, as claimed in claim 10, in which said guide means includes a second ring having a radially inner surface engaged with the radially outer surface of the rib on said first mentioned ring and also with the radially outer surfaces of said arcuate shoe portions; said first and second rings being independently rotatable; and a pair of support rings rotatably mounted in said casing in equal axial spacing to said first mentioned ring and peripherally supporting said second mentioned ring; said support ring having circumferential guiding surfaces engageable with the radially inner surfaces of the arcuate shoe portions of said guide shoes and radial guide surfaces engageahle with the axially outer radial edges of said arcuate shoe portions.

13. A rotary fluid machine comprising, in combination, a casing; at least one rotor rotatably mounted in said casing and formed with angularly spaced radial bores constituting cylinders; pistons reciprocable in each of said cylinders to vary the effective volumes of the cylinders to displace fluid relative to said cylinders; guide shoes each operatively connected to a respective piston; guide means surrounding said rotor and reciprocating said pistons upon rotation of said rotor; said guide means having an eccentricity relative to the rotor axis to define the piston strokes; said cylinders being arranged in at least two groups with the cylinders of each group having their axes in a respective common diametric plane through said rotor, said planes being spaced axially of said rotor; each of said guide shoes including a connection portion pivotally connected to the associated piston for pivoting of the guide shoe about an axis parallel to the axis of said rotor, said connection portion having dimensions such as to fit within the associated cylinder, a mounting portion extending outwardly from said connection portion, a bar extending from said mounting portion axially in both directions substantially parallel to their rotor axis, and a pair of circumferentially extending arcuate shoe portions each at a respective end of said bar; the cylinders in axially adjacent groups being staggered angularly with respect to each other so that, considered angularly, the cylinders of one group are intermediate the cylinders of the axially adjacent group; said guide means including a guide ring disposed between axially adjacent groups of cylinders and having a radially outer cylindrical guide surface engageable with the arcuate shoe portions on axially facing ends of the bars of the guide shoes of the two groups; said guide ring having flanges extending radially from opposite edges of said cylindrical surface and engageahle with the side edges of the arcuate shoe portions; said flanges being uniformly angularly slotted, in staggered relation with respect to the two flanges, to receive the bars of the guide shoes of the axially adjacent cylinder groups.

14. A rotary fluid machine, as claimed in claim 13, including a second guide ring engaged with the outer cylindrical surfaces of said flanges on said first mentioned guide ring and engaging the radially outer surfaces of said arcuate guide shoe portions; and a pair of support rings rotatably mounted in said casing and in uniformly axially spaced relation to either side of said first mentioned guide ring and peripherally supporting said second mentioned guide ring; said support rings having radially outwardly facing cylindrical guide surfaces engaging the radially inner surfaces of the arcuate guide shoe portions of the adjacent cylinder groups and having radially extending guide surfaces engaging the axially outer edges of the arcuate guide shoe portions of the guide shoes of the two axially adjacent cylinder groups.

15. A rotary fluid machine, as claimed in claim 11, in which said guide means includes a first cylindrical guide means and a second cylindrical guide means; said first cylindrical guide means including a first guide ring engaged with the piston guide shoes of the two axially inner cylinder groups; said second cylindrical guide means including a pair of second guide rings each engaged with the piston guide shoes of a respective one of the two axially outer cylinder groups; means for conjointly adjusting said first and second cylindrical guide means as to relative eccentricity; a first bearing supporting said first guide ring rotatably upon a ring member engaged by said adjustment means; a pair of second bearings each supporting a second guide ring, adjacent the axially outer end thereof; on the second ring member engaged by said conjoint adjustment means; and spacer means disposed between said first ring member and each of said second ring members.

References Cited by the Examiner UNITED STATES PATENTS 1,152,729 9/1915 Hele-Shaw 103-161 2,454,418 11/1948 Zimmermann 103161 X 2,503,614 4/1950 Eynard 103161 2,812,638 11/1957 Timms 103l61 X 2,895,426 7/1959 Orshansky 103-161 3,120,816 2/1964 Firth et al lO-3-174 X FOREIGN PATENTS 801,060 12/1950 Germany. 881,058 11/1961 Great Britain.

MARK NEWMAN, Primary Examiner.

LAURENCE V. EFNER, Examiner.

J. C. MUNRO, Assistant Examiner.

Claims

1. A ROTARY FLUID MACHINE COMPRISING, IN COMBINATION, A CASING; AT LEAST ONE ROTOR ROTATABLY MOUNTED IN SAID CASING AND FORMED WITH ANGULARLY SPACED RADIAL BORES CONSTITUTING CYLINDERS; PISTONS RECIPROCABLE IN EACH OF SAID CYLINDERS TO VARY THE EFFECTIVE VOLUMES OF THE CYLINDERS TO DISPLACE FLUID RELATIVE TO SAID CYLINDERS; GUIDE MEANS SURROUNDING SAID ROTOR AND RECIPROCATING SAID PISTONS UPON ROTATION OF SAID ROTOR; SAID GUIDE MEANS HAVING AN ECCENTRICITY RELATIVE TO THE ROTOR AXIS TO DEFINE THE PISTON STROKES; SAID CYLINDERS BEING ARRANGED IN AT LEAST TWO GROUPS WITH THE CYLINDERS OF EACH GROUP HAVING THEIR AXIS IN A RESPECTIVE COMMON DIAMETRIC PLANE THROUGH SAID ROTOR, SAID PLANES BEING SPACED AXIALLY OF SAID ROTOR; SAID ROTOR HAVING AT LEAST TWO EXTERNAL ANNULAR RADIAL RIBS EACH CENTERED AXIALLY ON A RESPECTIVE ONE OF SAID DIAMETRIC PLANES, THE AXIAL WIDTHS OF SAID RIBS BEING LESS THAN THE DIAMETER OF THE ASSOCIATED BORES; SAID GUIDE MEANS BEING FORMED TO PROVIDE RADIALLY INWARDLY OPENING ANNULAR GROOVES ARRANGED TO HAVE SAID RIBS EXTEND AT LEAST PARTIALLY THEREINTO; SAID BORES BEING FORMED THROUGH SAID RIBS TO PROVIDE EXTENDED GUIDE SURFACES FOR SAID PISTONS, WITH RESULTANT AXIAL SLOTTING OF SAID RIBS AT ANGULARLY SPACED LOCATIONS EACH CENTERED ON A RESPECTIVE CYLINDER AXIS; THE CYLINDRICAL SURFACE OF SAID ROTOR