US3697201A

US3697201A - Multiple rotors and control means thereto in fluid handling devices with working chambers or radially variable volume

Info

Publication number: US3697201A
Application number: US830246A
Authority: US
Inventors: Karl Eickmann
Original assignee: Individual
Current assignee: Individual
Priority date: 1969-06-04
Filing date: 1969-06-04
Publication date: 1972-10-10
Anticipated expiration: 1989-10-10

Abstract

This disclosure is related to improvements in fluid handling devices with working chambers of radially variable volume, such as pumps, motors, transmissions, compressores, engines or combustion engines of the vane type, radial piston type, gear type, trochoid piston type and the like, and the improvement consists in the provision of multiple rotor members and control means thereto. While one of the rotor members is a fluid handling member and another rotor member is a traction member. The rotor members are axially moveable relatively to each other and the control means includes thrust means for thrusting one of the rotor members against the respective stationary control face of the device.

Description

United States Patent Eickmann [451 Oct. 10, 1972 [54] MULTIPLE ROTORS AND CONTROL 3,327,477 6/1967 Stageberg ..4l8/ 133 MEANS THERETO IN FLUID 3,430,574 3/1969 Adelman ..4l8/ 133 g gg 'ffgfixgym g FOREIGN PATENTS OR APPLICATIONS VOLUME 230,241 3/ 1925 Great Britain ..4l8/l33 [72] Inventor: Karl Eicl 2420 Isshiki 900,188 9/1944 France ..4l8/135 f Kanagawa'ken Primary Examiner- Carlton R. Croyle apan Assistant Examiner-John J. Vrablik [22] Filed: June 4, 1969 Attomey-Michael S. Striker [21] Appl. No.: 830,246 [57] ABSTRACT This disclosure is related to improvements in fluid [52] US. Cl. ..4l8/132, 421880113835 21188012335 handling devices with working chambers of radially variable volume, such as pumps, motors, transmis- 5 g; 1 3? IlS, compress es, engines or combustion engines of e Ms/17,0 209:21 215 the vane type, radial piston type, gear type, trochoid piston type and the like, and the improvement consists in the provision of multiple rotor members and control [56] Reierences Cited means thereto. While one of the rotor members is a UNITED STATES PATENTS fluid handling member and another rotor member is a traction member. The rotor members are axially 3,357,362 12/1967 on ..9l/492 moveable relatively to each other d the control 858,594 7/1907 Gause et a1. ..4l8/ 133 means includes thrust-means for bx-sting one of the fielth rotor members against the respective stationary conmnavy t I face of the dev'c I 3,289,599 12/1966 Eckerle et al ..41s/132 e 1 3,291,053 12/1966 Gordon ..4l8/ 132 7 Claims, 19 Drawing Figures PATENTEIT i979 w 3.697.201

SHEET 1 BF 5 INVENTOR.

MR4 E/CKMAN/V MULTIPLE ROTORS AND CONTROL MEANS THERETO IN FLUID HANDLING DEVICES WITH WORKING CHAMBERS OR RADIALLY VARIABLE VOLUME One rotor member is located axially behind or before another or others and the rotor members are revolving with equal rotary angular velocity on the same shaft or axis. It is possible to fasten each rotor separately or indirectly relatively upon the shaft against rotation and providing the possibility of a limited axial movement of the respective rotor member relatively to the common shaft or axis. It is therefore possible, to locate control means, like fluid containing chambers to or in one or more of the rotor members and to utilize those control means to press at least one of the rotor members in an axial direction against a respective control face. The control means may also act for maintaining a close clearance or fit between the rotary and stationary control face of the machine. Due to the invention it is possible to fix one of the rotor members so to the shaft, so that it is prevented from rotation relatively to the shaft, but remains axially moveable in a limited extend, or one of the rotor members may be completely fixed to the shaft. It is now possible to provide at least one of the rotor members for tracting another rotor member or members to rotation in unison with the discussed rotor member or to clutch the said rotor member to another rotor member or members. The described rotor member may then be a tracting member, while another rotor member may be the fluid handling member of the machine and may be driven or tracted for rotation by said tracting member. Utilizing this improvement in fluidhandling devices with radially working variable chambers or variable working chambers, makes it possible to provide one or more fluid handling bodies in the machine and to associate a tracting member thereto for revolving the fluid handling rotor members or member and also to control the clearance between the control faces associated to the respective fluid handling member or members.

ln rotary fluid handling devices with radialwards variable working chambers, like gear pumps, vane pumps, trochoid pumps, radial piston pumps, machines, or motors it was difficult heretofore, to fasten the fluid handling rotary members on the driving or driven shaft of the machine, because fastening means, like keyways or splines would disturb the control face portion or cause the necessity of larger inner diameters of the control faces, which in turn would then cause greater control faces and thereby greater friction between control faces of the machine. Such draw back restricted the efficiency of such machines and restricted their power.

The main object of the invention is, to provide a tracting body and at least one working chamber containing fluid handling body onto a common shaft; to drive the tracting body by said shaft or to drive the shaft by said tracting body, to associate tracting means to the tracting body and at least one fluid handling body for forcing said tracting body and that at least one fluid handling body to revolve with equal rotary velocity in unison withthe axis of a common shaft.

It is another object of the invention, to provide control means into or onto one or more of the rotor member(s) of the main object of this invention for forcing one or more of the rotor members in axial direction into a suitable engagement to the neighboring body, especially to fix clearance between a stationary and a rotary control face to'the desired narrowness,:so that the leakage between those control faces is kept to a suitable minimum.

Still another object of the invention is, to provide a tracting rotor member onto a shaft; to provide a spline, key, rectangle or otherwise rotary traction providing clutch means between said rotor tracting rotor member and to provide each one fluid handling rotor member on each axial end of said tracking rotormember.

A still further object of the invention is to provide fluid containing pressure chambers, closure members and pressure means or spring means into or partially into said tracting rotor members or member.

Another object of the invention is to provide two or three rotor members between fixed faces of covers of a fluid handling machine.

A further object of the invention is, to adopt a separated rotor member against a rotor member and a working space of a gear pump or motor for revolving with said member in unison and for closing the working chamber(s) in one axial direction, and or to press members of the machine against other members.

It is another object of the invention to provide a rotor member to another rotor member in a vane type fluid handling device for revolving with the same in unison and or to close a working chamber or chambers in a rotary vane type machine in one axial direction and or to press a rotor member'or members of a vane type fluid handling device in an axial direction against a control body or its face. And it is another object of the invention to locate a rotor member between two vane type fluid handling devices in a machine for pressing both away from each other against the stationary control face of a respective member of the machine, and to said fluid handling device rotor members tracting same for rotation in unison or to clutch a traction rotor member and at least one or more rotor member of a vane type fluid handling device together.

A specially effective and powerful machine or fluid handling device is obtained by another object of the invention, which is to provide a tracting rotary member on a shaft of or through a radial piston machine and to clutch said tracting rotary member to one or more fluid handling rotary members of a radial piston machine. It is suitable and related to this object of the invention, to provide thrust members or thrust means in or through said tracting rotary member for thrusting said fluid handling rotor member or fluid handling rotor members axialwardly against a control body or control bodies. Effective and reliable fluid handling devices can be made by utilizing one or more objects of the invention either single or in combination. It is also possible to combine one or more objects of the invention with objects or features of others of my inventions or with conventional systems if such combination is carried out suitabley and in accordance with the laws of respective technology.

As referred to in the paragraph following the abstract of disclosure of this patent with regard to friction and efficiency of the devices mentioned thereunder, it has been managed in one of my earlier patents to overcome such difficulties, by making the rotor and driving or driven shaft of the same piece of material.

That, however, had a new drawback, that vibrations, shocks and the like onto the shaft resulted in welding or sticking between the control faces of the machine, because shocks from outside onto the shaft were transfered into the machine and via the rotor onto the control faces and the fluidfilm between he control face clearance(s). This difficulty is now also prevented according to this invention, because the driving shaft can now be made of a larger diameter at those places, where it bears the rotor member of members and in smaller diameter, in such area (s), where the control faces are outwardsof the shaft portion.

Space for means for retaining the rotor members or member for rotation in unison with the shaft is now also available due to the provision of the multiple rotor members of this invention.

BRIEF DESCRIPTION OF THEDRAWING 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. More details, features, embodiments and or objects of the invention may become apparant from the figures thereof.-

In the drawings:

FIG. 1 is a longitudinal sectional view through a machine with radialwards variable working chambers and two separated rotor members;

FIG. 2 is a cross sectional view through FIG. 1 along the line III-II;

FIG. 3 is a cross sectional view through FIG. 1 along the line III-III;

FIG. 4 is a longitudinal sectional view through a fluid handling device of embodiments of the invention;

FIG. 5 is a cross sectional view through FIG. 4 taken along the line V-V;

FIG. 6 is a cross sectional view through FIG. 4 taken along the line VIVI;

FIG. 7 is a longitudinal sectional view through another embodiment of a fluid handling device of the invention;

FIG. 8 is a cross sectional view through FIG. 7 taken along the line VIII-VIII;

FIG. 9 is a cross sectional view through FIG. 7 taken along the line IXIX;

FIG. 10 is a longitudinal sectional view through another fluid handling device, which is another embodiment of the invention;

FIG. 11 is a longitudinal sectional. view taken through another embodiment of a fluid handling device of the invention;

FIG. 12 is a cross sectional view through FIG. 11 taken along the line XII-XII;

FIG. 13 is across sectional view through FIG. 11 taken along the line XIII-XIII;

FIG. 14 is a Longitudinal sectional view through another embodiment of a fluid handling device of the invention;

FIG. 15 is an enlargement of a part of FIG. 14; and

FIG. 16 is an enlargement ofa part of FIG. 1 1;

FIG. 17 shows a longitudinal sectional view through another embodiment of a fluid means or rather thrust means of the invention; and

FIG. 18 is a longitudinal sectional view through another embodiment of a fluid handling device of the invention.

FIG. 19 is a longitudinal, but only partial view, as in FIG. 11, but demonstrating the provision of an additional embodiment of the invention into the device of FIG. 11.

In FIGS. 1 to 3 referential 1 shows the housing an referentials 2 and 3 show the covers of the housing of the machine or fluid handling device. Controlfaces 5 and 6 are provided inwardly on the respective covers 2 or 3 and constituting axial ends of a part thereof and thereby a controlface. These controlfaces are the stationary control faces. Fluid passages 20 and 22 extend through cover 3 and form control ports therein, which extend through controlface 5, while fluid passages 21 and 23 extend through cover 2 and form controlports therein, which extend through controlface 6. In the covers2 and 3 are bearings 24 provied wherein the driving or driven shaft 4 is rotatably borne. Shaft 4 is provieded with a tracting means or clutch, such as a key or spline 17 on one portion of shaft 4 and with a respective other tracting means 18 on another portion of shaft 4. Tracting means in this case shall means, that a coupling means means connects one of adjacent members or more for rotation in unison with shaft 4, or vice versa. Between the tracting or coupling means 17 and 18 is a bigger portion of shaft 4 provided, which is preferential circular for bearing rotormembers l5 and 16 thereon. Accordingto the invention, there is not one rotor, but there are two

rotor members

15 and 16 in this fluidhandling device of FIGS. 1 to 3.

Each

rotormember

15 and 16 is provided with a rotorhub which forms a seat suitable to be borne on the medial portion of shaft 4 and endwards of the rotor hub is a complementary tracting means member, which fits the

respective tracting member

17 or 18 of shaft 4. The

rotormembers 15 and 16 are now axially moved over shaft 4 until each

rotor member

15 or 16 engages from another end over shaft 4 into a

traction member

17 or 18 and is borne on the medial portion of shaft 4 between the

traction portions

17 and 18. Rotormembers l5 and 16 are now abutting each other with their backs and a space or recess or a plurality thereof may be formed between them, for example as shown at 19. The front ends of

rotormembers

15 and 16 of this invention are provided with plane or otherwise, for example conical or spherical end faces, which constitute rotary control faces. Said rotary controlfaces abutting and are sliding along the neighboring stationary controlface, for example in rotary controlface 7 along stationary controlface 5 and rotary controlface 8 of rotormember 16 along the stationary controlface 6. Rotormember 15 is provided with working chambers 9, whereto the rotor-passages 25 are leading. Rotorpassages 25 are extending from a respective working chamber in the

respective rotormember

15 or 16 through a portion thereof into and through the respective rotary contraolface 7 or 8. Displacement elements or pistons 11 are provided in the working chambers 9 of rotor member 15 and displacement elements or pistons 12 are provided in rotormember 16. The displacement elements 11 and 12 are in this embodiment of the invention provided with displacement guideshoes 14. Displacement actuator ring means 13 is provided for guiding the displacementguideshoes l4 and thereby the displacement elements 11 and 12 into and outward in the respective working chambers 9 or 10. Thus, fluid is suctioned into working chambers 9 through passage 20 or 22 and the respective controlports and rotorpassages 25, when the displacement elements 11 move outward in chambers 9 and the fluid is displaced or expelled from said chambers 9 in the opposite flow direction, when the displacement elements 11 move inwards in the working chambers 9. Fluid enters into working chambers when displacement elements 12 move outwards in said chambers 10 through passage 21 or 23 and the respective controlport thereof and through the respective passages, rotorpassages 25,

and fluid is expelled or displaced out of the working chambers or the respective working chamber 10, when the respective displacemrnt element 12 moves inwards in said respective chamber or chambers. The flow direction is thereby reversed.

Thrust means, fluid containing chambers or other chambers, springs, or the like, which are represented by reference numeral 19 may be provided between the rotormembers and 16 and or extend into one or both of them. The thickness of the

rotormembers

15 and 16 in axial direction is preferably so dimensioned, that the rotormembers 15 and 16, if abutting against each other with confronting endfaces, are just suitably fitting with a suitable clearance for operation between the stationary controlfaces 5 and 6 of housing covers 2 and 3. The

rotor members

15 and 16 are axially moveable relative to shaft 4, while they are prevented from relative rotational movement relative to shaft 4. They therefore revolve in unison with shaft 4, while they can axially move, for suitable low friction floating with their end faces, the rotary controlfaces 7, 8 between the stationary controlfaces 5 and 6. The latter stationary control faces 5, 6 may also be provided or abutting or inserted controlbodies, not shown if not directly provided on the covers 2 or 3. If the distance between the stationary control faces 5 and 6 is bigger than the sum of the axial thicknesses of the

rotor members

15 and 16, then the thrust means at 19 between rotor-

members

15 and 16 are provided for pressing the

respective rotor member

15 or 16 axially outwards for close contract of the rotary control faces 7 and 8 on the control faces 5, 6 due to the moveability in axial direction of both

rotormembers

15 and 16 leakage between the controlfaces 5 and 7 and 6 and 8 is thereby reduced to a minimum and thrusts or vibrations of blows onto shaft 4 from outside are not transfered from the shaft 4 to the rotormembers, because the latter are axially moveable and not fixed to shaft 4. At same time the thicker portion of shaft 4 between the

traction portions

17 and 18 provides a large radial bearing force for bearing highly loaded

rotor members

15 and 16 strongly on shaft 4. Thus, the machine of the embodiment of FIGS. 1 to 3 is a fluidhandling device, for example, pump or motor, of high pressure capability, high reliablity, simplicity and safety respectively to the prevention of friction or sticking between stationary and rotary controlfaces.

In the embodiment of the invention illustrated in FIGS. 4 to 6 to medial housing 42 has two outer housings 31 located outward of the respective ends of housing 42. Endcovers 32 and 33 are provided on the end of the outer housing '31.

Covers

32 and 33 are provided with bearings 54, wherein the driven or driving shaft 34 is rotatably borne. Coupling means 59 is provided on the medial portion of shaft 34 for tracting or being tracked to revolve together with medial rotor member 41 of this embodiment of the invention. Thus, medial member 41 and shaft 34 are forced to revolve in unison by coupling means 59, if the shaft 34 drives the rotormember 41 or if shaft 34 is driven by medial rotor member 41. Medial rotormember 41 may be axially moveable in a limited extent relative to shaft 34 and vice versa. In the sample of the FIG. 4 the medial traction portion 59 of shaft 34 is a hexagon and a suitably dimensioned hexagonal hole is provided in medial rotormember 41, so that these hexagons, or splines or key and keyways, which might be used instead of the hexagons, may constitute coupling means or traction means between medial rotor member 41 and shaft 34. On both sides of the medial rotor member 41 are rotormembers 45 and 46 provided. Rotary plates or discs 48 may be provided between the medial rotor member 41 and the outer rotor members 45 and 46. The outer rotor members 45 and 46 may be,'as in the figures, gears. They could also be trochoid inner rotors instead. The outer rotor members 45 and 46 are surrounded by outer gear rotor members 47 Outer rotor members 45 and 47 as well as 46 and 47 are thereby forming together internal gear pumps, as generally known in the art. The separating portions 49 are separating and sealing the working chambers 39 and 40 of the internal gear pumps from each other. One of chambers 39 and 40 is a lowpressure chamber, while the other is a highpressure chamber. Of these two chambers, one is the intaking expanding chamber, which takes the fluid in and the other is the expelling contracting chamber, which expels the fluid. An entrance passage 50 and an exit passage 50 extend through cover 33 into or from fluidhandling chamber 39 or 40 respectively. Similarly passage an exit passage and an entrance passage 51 extend through cover 32 into or from fluidhandling chamber 39 or 40 respectively. It should be realized, that in this embodiment of the invention there is one fluidhandling device adjacent each

cover

32 and 33. Each fluidhandling device consists mainly of inner gear rotor, outer gear rotor, separator 49 and fluidhandling chambers 39 and 40, whereof one is intaking and one is expelling fluid. In this example of the invention, there are therefore two internal geartype fluidhandling devices. One between cover 32, shaft 34, housing 31 and disc 48 or medial rotormember 41 and the other between cover 33, shaft 34, housing 31 and disc 48 or medial rotormember 41. The internal rotormembers 45 and 46 are borne on respective cylindrical portions of shaft 34 and the outer gear rotors 47 are borne in the respective housing 31. The separators 49 may be integral with or fixed to

covers

32 or 33 respectively. On the gear rotors or

trochoid rotors

45, 46 and 47 are the rotary controlfaces 37 or 38 provided. They slide tightly fitting along the stationary sealfaces or controlfaces 35 or 36 of

covers

33 or 32 respectively. On the other ends of the gear or

trochoid rotors

45, 46 and 47 are the medial discs 48 provided, which revolve in unison with rotormembers 45 and 46 and which close the respective adjacent working chamber 39 or 40 in one axial direction and which may also abut against the outer gear rotors or trochoid rotors and 47 or one of their respective and faces. Medial discs 48 may also be borne on the respective portion of shaft 34 and the rotormembers 45 and 46, as well as medial discs 48 and medial rotormember 41 may be in a limited extend axially moveable on shaft 34.

The medial rotormember 41 is provided with further coupling means, for example bolts, or pins 53 which extend through respective means to or into or through members 48, and or 45 and 46. In the sample of the FIGS. bores are extended through members

rotary members

41, 48, 45 and 46 with same axis. Pins 53 are inserted in such a bore and therefore forces

rotary members

45, 46, 41 and 48 to revolve in unison. There are a plurality of such boresand pins, as will be seen from sectional FIGS. and 6. Further more, according to this invention, there are bores 55 provided in the medial rotor member 41. But, they could also be provided in another rotor member, for example 48, 45 or 46. According to the invention, there are thrust members 56 and .57 provided in the bores 55 and spring means 58 may be provided between each a thrust member 56 and 57 and press them axialwardy away from each other Seal means 59 may be provided for sealing between a respective thrust member 56 or 57 and the wall of the bore 55 through medial rotormember. 41 and. other for sealing between a respective thrust member 56 or 57 and a medial rotordisc 48. Passages 52 extend through members 48 from a respective bore 55, so that during rotation of the rotormembers alternatively they communicate either with fluidhandling chambers 39 or 40 or pass over the separator 49. The radial crossection through the number of chambersor bores 55, which are at same time communicating with a respective fluidhandling chamber 39 or 40 is by the sum of crossections through said communicating chambers greater, than the radial crossection through the respective communicated working chamber 39 or 40. Therefore, fluid enters from the respective communicating chamber 39 or 40 into the respective bores or chambers 55, or if the chamber 55 is already filled with fluid, then the respective pressure is fluid in the communicating working chamber 39 or 40 extends into chambers 55, which are respectively communicating and, since the crossection through communicated chambers 55 is bigger, than the crossection through the communicating chamber39 or 40, the medial rotormembers disc 48 are pressed away from medial rotor 41 with its chambers 55 and against the respective adjacent rotormember 45 and] or 47 and or 46 and/or 47.

Thus, the fluidhandling chambers 39 or 40 are tighly sealed by the endfaces of medial discs 48. On the other hand, the medial discs 48 press against rotor members 45 and or 47 and or rotor members 46and or 47. Thereby the members 45 and 46 and/ or 47 are pressed against the

respective cover

32 or 33, so that the rotary sealfaces or controlfaces 37 or 38 of rotormembers 45, 46 and/ or 47 are pressed for tightly sliding and sealing against and along the respective stationary sealfaces or controlfaces 35 or 36. Thereby the fluidhandling chambers 39 and 40 are also sealed in the other axial direction. The bigger as the pressure in the chambers 39 or 40 respectively is, the bigger becomes the force which presses the said members and faces together. The force out of chambers 55, which are at the time communicating with a lowpressure space 39 or 40 is respectively small, while the force out of chamebers 55, which are at the respective time communicating with a high pressure chamber 39 or 40 are respectively great. Such, in the neighborhood of low pressure loaded chambers 39 or 40, the pressing force out of chambers 55, which presses said rotors and faces together, is low, while it is high in the neighborhood of high pressure loaded chambers 39 or 40. Thus, the forces'which press the said rotors and faces together, are ideal dimensioned and acting. They are high, where they need to be high and they are small, where they should be small in order to spare undesired friction. The actual force will be obtained by the actual dimensioning and location of the respective chambers or bores 55. Each of such bores during a revolution moves through a high pressure zone and through a low pressure zone, when the machine operates under power. In the cases, where the flows through the respective device

adjacent cover

32 or 33 should be separated or kept separated, so that a two-flow fluidhandling device is maintained or materialized, it is prefered to set a separationbody (not shown) in the drawing) into the respective chamber 55, so that chamber 55 is divided into two chambers, each one axially behind the other, ad so that fluid from the I one chamber in chamber 55 can not move into the other separated chamber in space or bore 55. Instead of gears, including internal gears, the device of FIGS. 4 to 6 could also be trochoid type fluid-handling device or a vane type fluid handling device. Instead of utilizing two pumps or motors or devices axialwardly of each/other, it would also be possible to utilize only one in the respective machine. Therefore an example" is given for demonstration and shown in FIGS. 7 to 9.

In FIGS. 7 to 9 the.

housings

61, 68 and 72 are provided with end covers 62 and 63. In covers 62 and 63 are the bearings 84 provided for rotatably bearing the rotary driving or driven shaft 64 therein. Shaft 64 has a bearing portion 64 prefered cylindrically configurated and a tracting or clutching portion 89. On the shaft 64 are the tractionrotormember 71 and the medial disc 67 and the fluidhandling rotormember borne and they revolve in unison with shaft 64. In order to force, that the shaft 64 and the said rotormembers revolve in unison, if one of the members revolves, the clutch means or traction meansv or members are provided. Shaft 64 has traction members 89, which engage in traction members 89 of the tractional rotormember 71. The said traction members may also be called clutch members.

Rotor members

67, 75 and 71 may still further be provided with other clutch members or traction members, for example bores and bolts, for example, bolts 83. They may extend into or through

rotors members

75, 67 and 71, so fast they are clutched together in tangential direction and they are forced to revolve together in unison if one of said rotormembers revolves. Thus, if one part of shaft 64 or

rotormembers

71, 67 or 75 revolves, the other of these also revolves, because if one revolves, then they revolve all in unison. Rotormember .75, may be, for example a gear, a trochoidbody, or, as in the drawing, a vanemachine rotor or another suitable fluidhandling body of a machine with radialwards variable fluidhandling chambers. One end of rotormembers 75 may be formed with an endface, constituting the sealface or controlface, called rotary seal face or contraolface 66 and the cooperating stationary controlface or seal face 65 may be provided on cover 63.

Passages

80, 81, 82 and 83 may extend through a member of the machine, for example through cover 63, so that they form controlports for communication with entrance or exit portions of

fluidhandling chambers

69 or 70. Vanes 74 may divide the

respective fluidhandling chambers

69 and 70 into intaking and expelling intervane spaces and thereby provide the intake and expellation of fluid. A bearing means or thrust bearing means 73 may be located between cover 62 and tracting rotormember 71. The traction-rotormember 71 is according to the invention provided with chambers or bores 76, which extend into or through the tracting-rotormember 71. Passages 80 may extend from the chambers 76 axialwardly or about axially through medial disc 67. Each one or more passages 80 extends from the respective single bore or chamber 76 through the medial rotary disc or rotormember 67, so that the respective chamber 76 is during rotation periodically communicated with intaking or expelling portion of

fluid handling chambers

69 and 70 or to a controlportion, or separating body portion therebetween. A cover member 77 is provided on the respective chamber 76 and axially moveable therein. Seal means may be provided between said covermember and the respective wall of the respective chamber 76. A spring means or thrust means 79 may also be provided for pressing the cover member 77 axially against the thrust bearing means 73. The sum of the crossectional area through the at a time communicated chamber(s) 76 must be, according to this invention, bigger, than the crossectional area through the portion of working

space

69 or 70, which is communicated through passage(s) 80 with the respective chamber (s) 76. Than the force of fluid out of the respective chamber (s) 76 is so big, that the medial'rotary disc 67 is pressed against the rotor 75 and the housing portion therearound and against the respective working

chamber

69 or 70. This force presses also suitably and effective the rotor 75 and the vanes 74,with the endfaces, the rotary seal faces or controlfaces against the cover 63 and its stationary sealface or controlface 65. Thus, due to the chambers 76 of this invention and the communication of them to respective fluidhandling space portions during rotation, the adjacent parts, covers, portions, faces or the like in the neighborhood of fluidhandling chambers are tightly pressed together for tigh sealing engagement. This action is obtained very economically, because the pressung force is never higher, that needed at the respective location and during a revolution the pressure in the respective chamber 76 changes between low and high in just such extend, at just such location as needed. The pressure forces can be suitably obtained by dimensioning and location of the respective chambers 76. It is also possoble to set seal bodies 78 into the chambers 76 for example in order to seal between rotary member 67 and the respective chamber 76 in traction-rotary member 71.

The machine of this embodiment as well as those of most other embodiments are very easily to be assembled and the shafts are capable of high radial load and they are simple in design and machining and sticking between rotary and stationary members is prevented, because the rotary members are freely moveable and adjustable on the shaft in a limited, but suitable extend, so that vibrations from outside or thrust onto the shaft are not transfered to the rotary parts and not transfered into the control-portions of the machine or against them.

Another embodiment of a fluidhandling device of the invention is demonstrated in FIG. 10. In this case there are 2 fluidhandling devices of my vane type machines provided between the

endcovers

102 and 103 of the machine. Bearings 124 are borne in the

covers

102 and 103 of the machine and they bear the rotatably mounted shaft 104. Shaft 104 has a medial traction portion or clutching portion 117 for clutching to respective cooperative clutchmeans 118 in the medial endovers 128 of the fluidhandling devices. Each rotor of such vane type fluidhandling device consists of a

rotormember

115 or 116, which is surrounded by a housing 113 for forming

fluidhandling spaces

109 or 110 therebetween, which are devided by the vanes (not shown in the drawing) into individual intervane spaces or fluidhandling spaces which during rotation of the rotormembers periodically intake and expell fluid. Endwards of the

rotors

115 or 116 are on each on end thereof the rotorendwalls 127 located. They may contain, as known from my other patents, slots for guiding the vanes and they are closing the working chambers and the individual intervane spaces therein in axial direction. Endwards of the rotorendwalls are the rotorendcovers 128 located. The rotor, rotorendwalls and rotorendcovers must revolve in unison, if a part of the machine revolves. Therefore, it is preferred to provide bores whereof each one bore in endcovers 128, endwalls 127 and

rotor

115 or 116 has the same axis, through the

rotor

115 or 116 and through the tehereto connected rotorendwalls 127 and rotorendcovers 128. Bolts 83 are inserted into those bores and thereby the

rotors

115 or 116 and the thereto belonging rotorendwalls 127 and the endcovers 128 are clutched together for revolving together in unison. The

covers

102 and 103 are distanced from each other by the therebetween located

housings

101 and 113. The thickness of the sum of the

housings

101 and 113 may thereby define the distance between the stationary controlfaces 105 and 106 on the

covers

103 and 102. The thisckeness of the sum of the

rotors

115 and 116 and of the edwals 127 and of the endcovers 128 may define and clearance between the rotoary controlfaces on the outer ends of two respective endvovers 128.

The rotormembers may either be kept togather by bolts, or they may be kept together by fitting between the controlfaces on the covers, as shown in this embodiment of the invention, in FIG. 10. Rotor passages 125 may extend from the individual intervane spaces of working

chambers

109 or 110 through rotor or 116 and an endwall 127 and an end wall 128 into the

rotary controlface

107 or 108.

Fluidpassages

120, 121, 122 and 123 may extend through

cover

102 or 103 and extend into a respective controlport in the stationary controlface 105 or 106. The fluid flows therefore into and out of the intervane spaces in working chambers with radialwards

variable volume

109 or 110 through rotorpassages 125 and passages to 123. Each one of the endcovers of each fluidhandling device is provided with a

rotary controlface

107 or 108, as is visible in the FIG. 10. The other endcover of each fluidhandling device is in this embodiment of the invention provided with a key means, clutch means or tracting means for receiving the keymeans, clutch means or traction means 117 all,

of shaft 104. Furthermore, each of the said other endcovers 128 may be provided with chambers of bores 119 for receiving closure members 112 therein, which are schsialwards moveable therein. spring means or thrust means 114 may be added. The said chambers or bores 119 could also, be extended into or through, or located in the respective endwall rotormember 127. Each chamber or bore 119 is communicated by a respective passage 180 to an intervane space of working

chamber

109 or 110 or to a respective slot in the rotormember or

rotormembers

115, 116, and or 127. Those slots in rotormemberscommonly in my inventions contain the vanes partially. Spring means or thrust means 114 may be associated to the respective closure member 112 in the respective chamber 119. Said thrust means or spring means 112 are pressing the closure member 112 in the respective space 119 away from the

medial rotor portion

115 or 116 and working

chamber

109 or 110, so that the closure member 112 moves axialwardly away in the respective space or chamber 119 and so, that the back of the closure member 112 is pressed against anadjacent member axialwardly of said chamber or space 119 and borne on said member. In the prefered embodiment if the invention of FIG. 10, the closure members 112 inside of spaces 119 of endcover 128 of the leftfluidhandling device are so borne and supported by the left endcover 128 of the right fluidhandling device and the closure members 112 in chambers 119 of the left endcover 128 of the right fluidhandling device are so borne and supported by the right endcover 128 of the left fluidhandling devide of FIG. 10. On the other hand fluid is passed-through the respective passage 180 into the respective chamber 1 l9 behind the respective closure member 112 therein, so that the action of the thrust means 114 is still supported by the pressure in fluid in the respective chamber 119. Theintensity of pressing the respective closure member 112 axialward against the inner endcover of the other fluidhandling device depends therefore mainly on the intensity of the pressure in fluid in the chamber" or space, whereto the chamber 119 is communicated and also on the crossectional area through the respective chamber 119. The pressure in the respective chambers 1 19 changes periodically during a rotation of the rotormembers of the fluidhandling device, because the respective individual intervane spaces of the working chambers change from intake to expel of fluid during a revolution and thereby in most occurances also between low pressure and high pressure. The pressure in the controlports and the neighborhood thereof between faces 105-107 and 106- 103 changes accordingly. The fluidhandling devices the left one and the right one in FIG. 10 are there fore pressed axially away from each/other with such force, as is justsuitable to press the rotary and the stationary controlfaces 105 to 108 just with such a force together, that leakage therebetween remains a minimum, while friction therebetween also remains a minimum, if the chambers 119 and the closure members 1 12 therein are correctly located, dimensioned and communicated.

Each one chamber 119 should preferably be communicated to a slot space and at least one chamber 119 to a respective individual intervane space. Those of the chambers 119, which are communicated to a respective slotspace may have high pressure at all times, if the slotchambers are continuously provided with high pressure. The vane machines of FIGS. 10 are basically known from my U. S. Pat. No. 2,975,716 but differ therefrom, that a plurality of vane machine-type fluidhandling devices is contained in the housing of FIG. 10, that the rotormembers of a plurality of van type fluid handling devices are axialwardly pressed away from each other and against respecive stationary controlfaces, that the spaces 119 are prodied and closure members are located therein (which may be sealed accordingly) and loaded with thrust means for pressing the rotor members of different fluidhandling devices axialwardly away from eachother, that at least one rotormember'is provided with a clutch means to the shaft, that at least one rotormember is .borne axialwardly moveable on a respective portion of the shaft 104 and that clutch means or bolts clutch. a plurality of rotormembers together and via the other clutch means to shaft 104, so that in practical operation of the fluidhandling device (s) shaft 104 and all rotormembers are forced to revolve in unison, if one of the members or the shaft rotates and that at same time each respective portion of the fluidhandling device in the neighborhood of a slot space or of an individual intervane space of working chamber(s) 109 or 110 is pressed so against the adjacent stationary controlface or 106 with such force, but not too high force, that effective sealing with less friction between adjacent rotary and stationary controlfaces is maintained during each revolution of the rotormembers, at which the pressure is fluid in the raseactice chambers 119 of this invention may periodically change. It is prefered, that the seats or fits of rotormembers of the machine relatively to the shaft 104 may be so, that effective radial bearing is assured, while axial moveablity respectively to the shaft 104 remaines maintained. Shaft 104 is a driving shaft, if the machine is a pump or compressor and is a driven shaft, if the device is a hydrostatically or otherwise driven motor. Medial rotormember end covers 128 may act as traction or clutch members and at the same time contain the the chambers 119 and the closure members or thrust members 1 12 or 114 therein.

In the embodiment of a fluidhandling device with radialwards variable working chambers of the invention, as shown in FIGS. 11 to 13 and FIG. 16, the housing 201 is proved with end covers or endcoverportions 203 and 202, which bear the

bearings

224 and 225 therein. In the bearings 224 as the shaft 204 rotatably borne and the bearings 254 fix the rotary shaft 204 in axial direction. Shaft 204 may be provided with a bore 264, which extends therethrough, so that a member of another machine or of an associated machine or vehicle may be xtended thereinto or therethrough. Shaft 204 may have a clutching portion, key portion or tracting portion 217 and, as preferably shown in the figure bearing portions endwards thereof. The said bearing portions may radially bear the

rotormembers

215 and 216, which are fluidhandling bodies, because they contain the working

chambers

209 or 210 respectively.Rotormembers 215 and 215 may be axially moveable on or respectively to shaft 204. To the keyportion 217 may be the rsdial rotormember 260 connected by means of the key portion, clutch portion or tracting portion 218 of rotormember 260 and rotormember 260 may sorround the keyportion 217 of shaft 204. Medial or tracting rotormember 260, which might also be called the rotorkeymember may also'be axially moveable relative to or on shaft 204. Rotormember 260 is therefore the medial rotormember, because it is located between the two

other rotormembers

215 and 216. Medial rotormember 260 is a key member, because it is the main member to key or clutchshaft 204 and the rotormembers 260,215 and 216 together for revolving together in unison, if one of them revolves and the rotormembers 215 and 216 are fluidhandling bodies or fluidhandling members, because they contain the respective radialwards variable working

chambers

209 or 210, which take in and expell the fluid during operation of the machine under power. Clutch, means, for example, like bores and pins or other clutching or tracting means or members, shown by referential 257 are provided for clutching either rotormember 215 or rotormember 216 to the medial rotormember 260. To provide bores and bolts into

rotormembers

260 and 215 or into

rotormembers

260 and 216, for example, as shown in the figure, is one of the easiest and inexpensiviest means for clutching a

rotormember

215 or 216 to the medial rotor member 260 and such clutching at same time maintains the axial moveability between the adjacent members, while it prevents relative rotary movement between them. Medial rotormember or keymember 260 may also be provided with bores 261, which extend into or preferedly through the medial rotormember 260 in axial direction. Each a communication passage 251 may extend through a portion of an adjacent rotor member for communication of the associated chamber or bore 261 with the associated

fluidhandling chamber

209 or 210 in

rotormember

215 or 216. A respective closure member 250 may be located in a respective chamber 261 and may be axialwardly moveable therein and sealed against the walls thereof. Thrust means 252 may be associated to the respective closure member 250 for pressing the same in axial contrary direction to the communicated working

chamber

209 or 210. Thus, the pressure in fluid contained at the respective time in the

respective fluidhandling chamber

209 or 210 presses the closure member 250 in the respective chamber 261 axialwardly away from the

rotormember

215 or 216 in which the respective fluidhandling chamber is contained and against the backward end of the

other rotormember

215 or 216, so that the

other rotormember

215 or 216 is pressed with its rotors controlface against the respective stationary controlface of the machine or machine member. Since chambers 260 are individually connected to either

rotormember

215 or 216 but individual chambers 260 are communicated to rotor 215 and others to rotor 216, it is assured, that both

rotormembers

215 and 216 are pressed for tight sealing engagement with less friction between the stationary controlfaces 205 and 206 and the rotary controlfaces 207 and 208. The fluid of chambers 210 by this arrangement of the invention presses the rotor 215 with its rotary controlface 207 against the associated stationary controlface 205, while the fluid in chambers 209 presses the rotor 216 in this arrangement of the invention with the rotary controlface 208 against the associated stationary controlface 206. Thus the fluid in the working chamber (s) of one rotor presses the other fluidhandling rotor into sealing sliding engagement with the associated stationary controlface. The location and dimensioning ofthe crossectional area through the respective chambers 261 must be suitable dimensioned, so as to obtain anough'force for-pressing the adjacent rotor into tight sealing engagement with the associated stationary controlface, but also so dimensioned, that the force remains law enough to prevent to high friction between the co-operating controlfaces. Sealmembers 253 may also be provided in the chambers 261 for sealing the same against the rotormember with the fluidhandling chamber, whereto the space 261 is communicated. Seals 254 may be provided for sealing between a rotor and seal member 253. Seal 255 may be provided for sealing between a Sealmembers 253 and seal 256 may be provided for sealing between closuremember 250 and wall of the respective chamber 260. If there are seal members 253 provided, then they should be provided with a passage (s) 256. The sample of members, which may be provided in bores of chambers 260 are shown in an enlarged scale in FIG. 16. This arrangement is however by way of example only.

Rotorpassages 225 extend from the respective working

chamber

209 or 210 through the

respective rotormember

215 or 216 in an axial or substantial axial direction into the respective rotary controlface 207 or 208.

Fluidpassages

221 and 223 extend through a cover f.e.202 of the machine into the stationary contrilface 206 and form controlorts therein.

Passages

243 and or 244 respectivels may extent and communicate from the

port

220 or 222 to the

respective controlport

220 or 220 in the respective controlface 205.

Passages

243 and 243 may either extend only through the cover 203 or through the cover 203 and housing 201 and or they may even additionally extend through the endcover 202. The flow of fluid into and out of the respective working

chambers

209 or 210 occurs accordingly through the thereto connected passages of the passages cited herebefore. Displacement members, for example pistons or the like, 211 or 212 may be extended into the respective. fluidhandling chambers 209 or 2l0 and may be actuaed by fluid therein or by the actuator means 203 via the displacement member guides or piston shoes 214 to move inwards and /or outwards in the respective working chamber 209' or 210, whereby the volume of the working

chambers

209 and or 210 varyfies in radial direction periodically during a revolution of a rotormember. Actuator means 213 may be stabilized by supports 245 and borne thereby in bearings 442. Adjustment means 240 may be guided in slides 241 for varyfying or adjusting the dosplacement stroke of the displacement members 1 1 or 212.

The embodiment of a fluidhandling device of the invention shown in FIG. 14 is about similar to that shown in FIGS. 11 to 13 and the referentials with the same two digets on the end of the referential are shown similar parts as in the embodiment of FIGS. 11 to 13. In the embodiment of FIG. 14 it is however more clearly and more larger shown, how the tracting bolts 357 may be inserted into the respective bores in the medial rotormember 360 and into thevrespective bores in the

rotormembers

315 and 315 for clutching rotormembers 315 and 316 to medial rotormember 360 and now the clutching bolts 357 a preferably locate and configurated. The guide ring 370 is assembled in the actuator means 313 for guiding the piston shoes or displacement member guides 314 suitably. As difference to the embodiment of FIG. 11 the embodiment of FIG. 14 has the working chambers of two different rotormembers axially behind eachother. That" means, that chambers 309 of rotor 315 are axialwardly in front or behind the chambers 310 of rotor 316.

Thechambers

209 and 210 of

rotors

215 and 216 of FIG. 11 were not being each other,but in an angle between eachother. Both arrangements are not noval, but both have several features disadvantages which should be considered at the design of the machine. The chambers angularily between eachother have-the feature of uniform flow and compactness of the machine. The chambers behind each other have the feature, that there is enough space in the rotors for setting the clutch bolts 357. Another feature of the chambers behind eachother is, what two chamber, each one in a different rotor, for example a chamber 309 of rotor 315 and a chamber 310 of rotor 316 need together only one bore through medial rotormember 360. The bore 361 is than common to both

chambers

309 and 310 which are beding or before eachother, but in

different rotors

315 and 316,

passages 351 are communicating the

respective chamber

209 or 310 with the bore or chamber 361 in medial rotor 300.

FIG. 15 shows an enlargement of a chamber 361 of medial rotor 360 of FIG. 14 and of the members therein an associated thereto an the neighboring portions of parts or rotormembersThe arrangement is by way of example only. In this case there are two sealcovers 353 located in the bore 361, both inoppositional axial direction. Passages 356 extend through them. Seals 355 may be provided for sealing between sealcovers 355 and the wall of chamber or bore 361. Seals could. also be provided between the respective cover 353 and the adjacent rotormember endwall of

rotor member

315 or 316 for sealing the respective passage 351 and the internal space portion between the covers 353 in chamber or bore 360 against losses or income from the outside. Thrust member 352 may be inserted between the cover members 353 for pressing the same away from each other and against the respective endface of the respective

adjacent rotor member

315 or 316. Disloading spaces also be formed on the covermembers 353. In action of the machine, fluid passes from a respective communicated working chamber 309 in rotor 315 through passage 351 into chamber 361 and from the respectively communicated chamber 310 in rotor 316 through the respective passage 351 into the space between covers 353 in bore or chamber 361. As far as in the sentence before it was said fluid flows, this shall also mean, that if no fluid flows, because all respective spaces and passages are already filled with fluid, that the pressure wave extends in the respective way into the chamber 361. It is known, that pressure in fluid also moves or flows, f.e. with the sonic velocity of the pressure wave. This move of the pressure waves must be considered in machines of this invention with high rotary angular velocity, because the delay in extension of pressure in fluid may cause delay in the pressing action, out of the respective chamber 361. The case of FIG. 11 of

chambers

309 and 310 axially behind or before eachother has the other feature, that both

rotors

315 and 316 are at sametimes pressed locally with samepressures or force against the respective stationary controlfaces. On contray thereto in the FIGS. 11 to 13 with the chambers 309 angularily spaced between chambers 310 the pressing of local portions of the

rotors

315 and 316 against the stationary controlfaces does not occur at same same time locally with same force, but at different times. The arrangement of FIG. 15 is specially conventient, if both flows of fluid, which flow through

fluidhandling rotors

315 and or 316 are of same pressure in fluid. If however, both rotors, 315 and 316 would handle each a flow of fluid of different pressure respetively to the other, then the flows would have to be kept separated from eachother and then it wouldbe necessary, to provide a sealing wall between both rotormembers 353 in FIG. 15. Suchsealing wall (not shown in the drawing) would have to fit in the walls of chamber 361 for dividing this respective chamber 361 into two axially behind eachother located chambers, whereof one must be communicated to a chamber 309 and the other to a chamber 310. At least one or both covermember 353 must be kept freely moveable relatively to such sealing wall, so that the covers 353 can still freely move axially in chamber-361 for beeing pressed against the

respective rotormember

315 or 316 for pressing the same away from the other and against the respective stationary controlface of the machine. Flow from one chamber of the two chambers which are sealed from each other by the sealing wall into the other must be prevented in cases of different pressures in different flows through the machine. The said, and not shown shown, sealing walls could be discs of a diameter corresponding to the diameter of bores 361 in member 360 for fitting tightly therein. Seals could of course be added. The configuration and location of members in FIGS. 15 and 16 are also by way of example only. Suitably dimensioned members of other design could also be used, if they are so applied as to material the aim and action of the invention.

As far as fluidhandling devices with radial variable working chambers are shown or cited in this specification those shall include all those fluidhandling devices, wherein the working chambers vary theiy volume not achialwardly but radialwardly. Those machines are for example radial piston pumps and motors, gear pumps, internal gearpumpsv and motors, trochoidpumps and motors, vane pumps and motors or the respective compressors, airmotors, steam motors, gas motors or combustion engines. As far as on one or the otherv type of those fluidhandling devices an embodiment of the invention is demonstrated in this specification it should be realized, that the embodiment could also be utilized in certain cases on others of fluidhandling devices with radially variable working chambers. That means especially, that embodiments of one of the FIGURES could under certain conditions be exchanged into one or more of the other FIGURES. Especially as far as machines with only one fluidhandling system are shown in the drawings they could be similarily converted into multiple fluidhandling devices, if suitably and in accordance with other embodiments, design would be made. And as far as multiple fluidflow devices are demonstrated, they might also be utilized as single flow devices, if suitably designed with features of other embodiments of the invention. The invention applies to two or more rotormembers and a third member, which might be a shaft.

The invention makes the production of fluidhandling devices more inexpensive and makes the governing of the controlnmeans between stationary and rotary parts more effective and reliable. Thus an inexpensive and reliable and effective fluidhandling devices method is achieved by the present invention and it is desired that the patent shall not be limited to the specific embodiments shown in the drawings, but shall cover whatever patentable novelty resides in the invention. The invention shall therefore be only restricted by the accompanying claims.

The cover means for example 250,253,353 etc., may be provided with disloading recesses for example 367 or 267 and'said disloading recesses may be communicated, i.e. by

passages

268 or 368 to spaces under less pressure, so that the cover means remain always under pressure load from

space

260 or 360 etc. and remain thereby pressed against the adjacent rotormember.

In FIG. 17 the thrust chamber 451 in tracting rotor member 260 contains a medial dividing wall member 451 which can also be integral with tracting rotary member 260. Seats for spring means 451 may be provided for guiding the thrust means 451 and to prevent that portions thereof could under centrifugal force during rotation of port 260 accidentially enter into the clearance between the medial wall member or seal bloc 451 and the closure members 250.

Closure members

250, 253 and the neighboring members may be and act similar as those in FIG. 16.

In FIG. 18 is demonstrated, that the tracting rotary member 460 is clutched by means 664 to. shaft 464 for revolving therewith in unison and also axially moveable clutched by means 457 to fluid handling rotary member 415 for tracting the same to revolve with the tracting member 415 and shaft 464 in unison. Thrust chambers 461 are located in the tracting rotary member 460. They are communicated by passages 458 to the respective fluid handling chambers 409. Closure members 253 are providing the closing of chambers 461 in one axial direction and also the sealing of passages 458 between

rotary members

415 and 460. Closure members 250 are closing the respective thrust chambers 461 in the other axial direction. Closure members 250 are axially borne on another rotary member 471 which revolves and is borne axially on a thrust bearing means 473. Shaft 464 is borne in bearings 424 in the housing or covers 402, 403 thereof.

The housing or cover 403 conatins the entrance and exit passages 420 and 422 and is provided with the stationary control face 482. Fluid handling rotor member 415 is provided with the rotor passage 425 and the rotary control face 482. Passages 425 lead fluid from the ports in the control faces to the working chambers 409 and therefrom back through the control faces 481 and 482 into the exit passage 420 or 422.

All

rotary members

415, 460, 471 and the thrust bearing 473 may be fitted or inserted between the

covers

402 and 403 and be borne on revolvable shaft 464. In case of fitting them between the

covers

402 and 403 springs are needed in the thrust chambers. There can however be also a clearance axially between the rotary members and covers. It is then possible, to provide shaft 464 with a spherical portion 564 for bearing the fluid handling rotary member tehereon:

Fluid or pressure in fluid is passed from the respective fluid handling working chamber 409 through communication passage means 458 into the respective fluid containing thrust member chamber 461. Thereby the respective closure member 250 is pressed against rotary member 471 and rotary member 415 is pressed against control face 482 of cover 403, because'the pressure in fluid in the respective thrust chamber 461 presses the closure members away from each other and closure member 253 against rotor 415 and thereby rotor 415 against cover or control body 403.

More details of sizes and actions respectively sections of thrust chambers and or thrust members or clo-' sure members there in can be obtained from my US. Pat. No. 3,398,698 and especially from FIGS. 15 to 18 thereof.

In former fluid handling devices of radial piston machines with axial fluid flow the thrust chambers were contained in the fluid handling rotors and the fluid handling rotor head seats on the shaft. Thereby axial movement of the rotor of the shaft was possible. But spherical movement and rotary fraction of the rotary fluid handling body was limited or impossible. That caused welding between the control faces and made the fluid handling devices thereby inoperable, because the rotors could not adjust themselves enough to the stationary control faces or face.

This drawback of the former devices is completely overcome by this invention and welding between the control faces is prevented, because rotor 415 can spherically swing andaxially move on the spherical portion 564 of shaft 464, so that fluid handling body 415 is suitable and able to adjust itself in and onto the stationary control face 482. The rotary traction is separated from the bearing of fluid handling rotor 415 on shaft 464, so that the former clutching of the fluid handling rotor to the shaft is prevented and can'no more disturb the free adjustment of the rotor onto the stationary controlface. Also the rotary traction force is strengthened because the clutch means between the separated tracting rotor and shaft can be made strong without disturbing the adjustability of the fluid handling rotor. The fluid handling device of this invention became thereby safe and effective in operation and the former welding between the control face is prevented by the invention.

The fluid handling device becomes also more inexpensive, because the fluid containing pressure chambers in the tracting rotary member can be simply machines as simple bores. Also the same tracting rotary members and the same fluid handling rotary members can be selectively supplied either to FIG. 11 or to FIG. 18. FIG. 18 is a partial longitudinal sectional view through a portion of a fluid handling device which shows embodiment of the rotary members and control means, like tracting members and thrust means of the invention.

Traction rotor 460 is clutched by clutch 664 to shaft 464 and traction rotor 460 is clutched axially to working rotor 415 by axially moveable clutch means 457. 7

Closure devices 250 are achsially moveably inserted into chambers 461 of traction rotor 460 and they are borne on a rotary member or rotor means 471, which revolves on an achsial thrust bearing means 473. The thrustbearing means 473 is borne on housing or cover portion 402. Thus, the working rotor 415, the traction rotor 460" and the bearing rotor 471 are inserted between housing or cover portion 403 and bearing means473 of housing or voverportion 404. Rotor 471 revolves in unison with tractionrotor 460 and fluidhandling rotor 415. The reaction forces of fluid under pressure in chambers 461 press rotor 415 against member 403 with controlface 482, so that

controlfaces

482 and 481 seal and slide along eachother and press closuremembers 250 against rotor 471 and rotor 471 against bearing 473404.'Thus, the fluidhandling rotor 415 is free to slide and adjust itself along controlface 48s, while it is driven by traction rotor 460 and clutch means 457. The members of this embodiment are safe in operation and simple in manufacturing. The assembly of traction rotor and separated fluidhandling rotor makes it possible, to bear the fluidhandling rotor 415 on a sphaerical bearing portion 564 of shaft 464, so that the fluidhandling rotor 415 can adjust itself achsially and spherically, a feature which could not easily be acheaved, if no separated traction rotor would be supplied. But such movement is assential for smooth and safe operation of

controlfaces

481 and 482 of the fluid-v handling device.

FIG. 19 shows a partial sectional view through FIG. 11 and demontrates the insertion of a passage means into the device of this embodiment of the invention. Passage means 298 is extended from fluidhandling chamber 210

throughfluidhandling rotors

216 and 215 and through traction rotor 260 into-clearance or space 296 on the other end of the opposite rotor for passing fluid thereinto in order to balance the rotors for suitable operation at different fluid pressures in different working chambres. Passage member 297 extending through 260 and into 215 and 216 makes this possible. A similar passage from chamber 209 to chamber or clearance 299 is shown on the bottom portion of the FIGURE. Thereby pressure of both worling chamber groups acts in both control clearances on rotorends of

fluidhandlingrotors

215 and 216. The device can now operate at different pressures in different groups.

What is claimed is:

1. In a fluid handling machine, in combination, housing means including a central portion, and two end cover means having confronting stationary control faces, each cover means including inlet and outlet means for a fluid having inlet and outlet ports on said stationary" control faces; shaft means mounted in said cover means for rotation; at least three rotary means mounted on said shaft means within said central housing portion and including two outer rotary means having opposite rotary control faces cooperating with said stationary control faces in sealing contact, and a medial rotary means between said two outer rotary means; annular means surrounding said outer rotary means and forming high pressure and low pressure working chambers with the same, said rotary control faces forming control ports successively connecting said inlet and outlet ports of said stationary control faces, respectively, with said working chambers,'respectively; coupling means for connecting said three rotary means and said shaft means for rotation together, for limited axial movement of said three rotary means relative to each other and to said shaft means, and fluid pressure thrust means in said medial rotary means communicating durmg rotation with said hig pressure and low pressure working chambers and exerting axial pressures against said outer rotary means for pressing said rotary control faces against said stationary control faces with a great force in the region of said high pressure working chamber and with a lesser force in the region of said low pressure working chamber whereby leakage is prevented.

2. The device of claim 1 wherein said coupling means include first key means on a central portion of said shaft, second key means in a central opening of said medial rotary means engaging said first key means for mounting said medial rotary means for limited axial movement on said shaft, and axially extending bolts passing through said three rotary means for connecting said outer rotary means for rotation with said medial rotary means and said shaft.

3. The device of claim 1 wherein said thrust means include thrust chambers in said medial rotary means communicating during rotation of said three rotary means with said working chambers so that the pressure acting in said thrust chambers for pressing said outer rotary means with said rotary control faces against said stationary control faces is the saine as the pressure at the same moment in the working chamber communicating with said thrust chamber.

4. The device claimed in claim 3 wherein said medial rotary means has a bore therethrough; wherein said thrust means include thrust members in said bores forming said thrust chambers and receiving pressure fluid from said working chambers for pressing against said outer rotary means.

5. The device of claim 4 wherein each said thrust means include a pair of thrust members in each bore so that said bore is closed at both axial ends, said closure thrust forming together said thrust chambers.

6. The device of claim 5 including spring means in said thrust chambers for urging said thrust members apart and against said outer rotary means.

7. The device of claim 5 comprising discs located between said medial rotary means and said outer rotary means and having central openings through which said shaft means passes; wherein said discs have narrow bores therethrough registering with said bores of said medial rotary means;vand wherein said coupling means connect said discs with said outer and medial rotary means for rotation.

Claims

1. In a fluid handling machine, in combination, housing means including a central portion, and two end cover means having confronting stationary control faces, each cover means including inlet and outlet means for a fluid having inlet and outlet ports on said stationary control faces; shaft means mounted in said cover means for rotation; at least three rotary means mounted on said shaft means within said central housing portion and including two outer rotary means having opposite rotary control faces cooperating with said stationary control faces in sealing contact, and a medial rotary means between said two outer rotary means; annular means surrounding said outer rotary means and forming high pressure and low pressure working chambers with the same, said rotary control faces forming control ports successively connecting said inlet and outlet ports of said stationary control faces, respectively, with said working chambers, respectively; coupling means for connecting said three rotary means and said shaft means for rotation together, for limited axial movement of said three rotary means relative to each other and to said shaft means, and fluid pressure thrust means in said medial rotary means communicating during rotation with said high pressure and low pressure working chambers and exerting axial pressures against said outer rotary means for pressing said rotary control faces against said stationary control faces with a great force in the region of said high pressure working chamber and with a lesser force in the region of said low pressure working chamber whereby leakage is prevented.

3. The device of claim 1 wherein said thrust means include thrust chambers in said medial rotary means communicating during rotation of said three rotary means with said working chambers so that the pressure acting in said thrust chambers for pressing said outer rotary means with said rotary control faces against said stationary control faces is the same as the pressure at the same moment in the working chamber communicating with said thrust chamber.

7. The device of claim 5 comprising discs located between said medial rotary means and said outer rotary means and having central openings through which said shaft means passes; wherein said discs have narrow bores therethrough registering with said bores of said medial rotary means; and wherein said coupling means connect said discs with said outer and medial rotary means for rotation.