US3829256A

US3829256A - Displacement machine

Info

Publication number: US3829256A
Application number: US00312479A
Authority: US
Inventors: H Guttinger
Original assignee: Aginfor AG
Current assignee: Aginfor AG
Priority date: 1971-12-10
Filing date: 1972-12-06
Publication date: 1974-08-13
Anticipated expiration: 1991-08-13
Also published as: ES409449A1; DK135641B; FR2164247A5; HU173554B; NL7215337A; DE2230773B2; NO136548B; DE2230773A1; CH561842A5; AU4987472A; DK135641C; NO136548C; AT314358B; CS185614B2; GB1380760A; CA969028A; AU460223B2; SE388462B; JPS4866207A; IT971039B

Abstract

A displacement machine comprising a displacement chamber subdivided into at least two series connected consecutively arranged chamber sections. Each of the chamber sections is bounded by an outer and an inner substantially cylindrical jacket sector and by two substantially planar closure surfaces. A displacement device is arranged to carry out a revolving movement and has a respective substantially cylindrical sector-shaped vane located in each of the chamber sections of the displacement chamber. Each of the vanes has longitudinal edges and curved surfaces, each of said vanes, independently of its momentary position and during the course of the revolving movement, contacting by means of said longitudinal edges the planar closure surfaces and at least with one of its curved surfaces the associated cylindrical jacket sector of the associated chamber section along a contact line. Each of the chamber sections of the displacement chamber and each of the vanes of the displacement device span an angle of at least 270*, and that a chamber section and the therein arranged vane is angularly shifted with respect to the next connected chamber section and its vane by the complement of said span angle for 360*.

Description

United. States Patent [191 Giittinger [111" 3,829,256 Aug. 13, 1974 DISPLACEMENT MACHINE [75] Inventor: Heinrich Giittinger, Wettingen,

Switzerland [73] Assignee: Aginfor AG fur industrielle Forschung [22] Filed: Dec. 6, 1972 [21] Appl. No.: 312,479

[30] Foreign Application Priority Data Dec. 10, 1971 Switzerland 18082/71 [52] U.S. Cl. 418/5, 418/59, 418/210 [51] Int. Cl. F04c 1/02 [58] Field of Search 418/59, 5

[56] References Cited UNITED STATES PATENTS 801,182 10/1905 Creux 418/59 X 3,125,031 3/1964 Rydberg... 3,494,293 2/1970 Braun 418/59 FOREIGN PATENTS OR APPLICATIONS 825,643 3/1938 France 418/59 486,192 5/1938 Great Britain 418/59 Primary Examiner--C. J. Husar Assistant Examiner-Leonard Smith Attorney, Agent, or Firm-Craig & Antonelli 57 ABSTRACT A displacement machine comprising a displacement chamber subdivided into at least two series connected consecutively arranged chamber sections. Each of the chamber sections is bounded by an outer and an inner substantially cylindrical jacket sector and by two substantially planar closure surfaces. A displacement device is arranged to carry out a revolving movement and has a respective substantially cylindrical sectorshaped vane located in each of the chamber sections of the displacement chamber. Each of the vanes has longitudinal edges and curved surfaces, each of said vanes, independently of its momentary position and during the course of the revolving movement, contacting by means of said longitudinal edges the planar closure surfaces and at least with one of its curved surfaces the associated cylindrical jacket sector of the associated chamber section along a contact line. Each of the chamber sections of the displacement chamber and each of the vanes of the displacement device span an angle of at least 270, and that a chamber section 8 Claims, 7 Drawing Figures DISPLACEMENT MACHINE BACKGROUND OF THE INVENTION The present invention relates to a new and improved construction of displacement machine embodying a displacement compartment or chamber subdivided into at least two series connected consecutively arranged chamber sections, each of which is bounded by a respective outer and inner cylindrical jacket sector as well as by two planar or flat closure surfaces. The displacement machine further comprises substantially cylindrical sector-shaped vanes of a displacement device designed for carrying out a rotatory movement and which vanes are arranged in the chamber sections of the displacement compartment, and further wherein, each of the vanes, independently of its momentary position during the course of the rotatory movement, contacts by means of its longitudinal edges the planar closure surfaces and with at least one of its'curved or domed surfaces the confronting cylindrical jacket section of the associated chamber section along a contact jacket line.

Machines withrotatory or circulating displacement devices have, according to a newly employed nomenclature or designation in the art, also been referred to as circular piston machines to express the fact that the displacement device (piston) carries out a rotatory or circulatory movement, that is to say, a movement wherein each point of the displacement device describes a complete circle, and all circles have the same diameter. In contrast thereto there are the rotational piston machines in which the displacement device (or piston) carries out at least a rotational movement which can be superimposed upon a circulatory movement, so that there is produced a type of rolling-off movement of the displacement device in the displacement chamber or compartment.

In the event that the displacement device is mechanically driven then such type machine functions as a pump; on the other hand if the displacement device is driven by a fluid medium which flows through the machine then, in the broadest sense, it operates as a motor, wherein under this expression there is also tobe understood a throughflow measuring device.

Displacement machines similar to the previously mentioned type are known to the art in a number of different constructional variations. For instance, so-called spiral pumps (and motors) have become known to the art in which the displacement device possesses the form of a spiral with at least one convolution, and the displacement compartment likewise possesses the form of a spiral, the radial width of which corresponds to the diameter of the circular movement plus the wall thickness of the displacement device. What is particularly disadvantageous with such type spiral pumps is, above all, the extremely difficult manufacturing operations required, because the ideal spiral shape only can be approximately produced with conventional equipment and this approximation does not satisfy the degree of accuracy needed by its operational principle. This also seems to be a reason why the spiral pumps, with very few exceptions, have not previously been widely accepted.

Therefore, there have also been proposed to the art displacement machines with a single cylindrical arcshaped displacement device. With such machines the greatest difficulties arise on account of the sealing between the ends of the displacement device and the associated wall of the displacement compartment, while the sealing problem at the side edges and along the jacket surface of the displacement device has been solved satisfactorily because the surfaces which during contact function in a sealing manner are either flat or cylindrical surfaces and always contact approximately at the same angle of attack, and moreover, constitute surfaces which can be readily manufactured with the greatest accuracy. This is not so for the ends of the cylindrical jacket are because such ends only contact an associated compartment wall during approximately one-half of the circulatory movement. Additionally, these ends do not tangentially contact the associated compartment wall during the entire contact phase, as such is the case for the contact lines between cylindrical surfaces. Quite to the contrary, the angle of attack of the ends changes during the contact phases from 0 to and again to 0.

There is already known to the art a displacement machine of the previously mentioned type in which, through a series connection of the sections of the dis placement compartment, there: is attempted to overcome the problems of sealing the corresponding vanes (sections) of the displacement device.

However, with such constructions there is established at a certain momentary position of the displacement device, a direct connection of the inlet and outlet, so that the efficiency of the machine is considerably reduced because the machine, employed as a pump or motor respectively, conveys or drives respectively, in surge-like fashion.

Hence, with the known machine, duringmovement of the displacement device from one momentary position into a further one, there is changed the displacement-effective compartment volume, so that the machine automatically only allows throughput of compressible media.

Also the change of the displacement-effective compartment volume contributes to the above-described surge-like operation, that is to say, the medium flowing through the machine is not subjected to any continuous throughput, as such for instance is the case with fluid flow machines.

SUMMARY OF THE INVENTION Hence, it is a primary object of the present invention to provide an improved construction of displacement machine which is not associated with the aforementioned drawbacks and limitations of the prior art constructions and effectively and reliable fulfills the existing need in the art.

Another important object of the present invention relates to a new and improved construction of displacement machine of the aforementioned general character, in which there are not only overcome the sealing problems between the ends of the displacement device and its vanes and the associated walls of the sections of the displacement compartment, but at the same time there is ensured for a continuous surge-free throughput of the conveyed or taken-up medium, respectively, without having to take into account any limitations with regard to the compressibility of the .medium.

Now in order to implement these and still further objects of the invention, which will become more readily apparent as the description proceeds, the displacement machine of this invention is generally manifested by the features that each of the chamber sections of the displacement chamber or compartment and each of the vanes of the displacement device span in known manner a spanning angle of at least 270, and that a chamber section as well as the vane arranged therein is arranged in rotated or angularly shifted manner, through the 360 complement of the span angle, with regard to the next connected chamber section and its vane.

BRIEF DESCRIPTION OF THE DRAWINGS The invention will be better understood and objects other than those set forth above, will become apparent when consideration is given to the following detailed description thereof. Such description makes reference to the annexed drawings wherein:

FIGS. 1 and 2 respectively show in markedly schematic illustrations a simple constructional embodiment of displacement machine designed according to the invention with two similar displacement vanes rotating in the same sense and depicted in two respective different movement phases;

FIGS. 3 and 4 illustrate an embodiment of displacement machine, similar to the showing of FIGS. 1 and 2, but this time having three similar displacement vanes, likewise showing same in two different movement phases;

FIG. 5 illustrates an embodiment of the displacement machine with four similar displacement vanes;

FIG. 6 illustrates a further embodiment of displacement machine with four displacement vanes, but with a displacement compartment or chamber only divided into two sections; and

FIG. 7 is an exploded view of a practical exemplary embodiment of displacement machine designed according to the principles of FIGS. 1 and 2.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Considering now the drawings, it is to be remarked that in conjunction with the various illustrations of FIGS. 1 to 6 the displacement vanes have been depicted with thick full lines and the walls of the compartment with thin full lines provided at one side with crosshatched lines. The contact lines between the displacement vanes and the compartment walls have been portrayed with a clearly marked point.

Turning now more specifically to the exemplary embodiment of displacement machine depicted in FIGS. 1 and 2, there will be recognized a displacement compartment or chamber subdivided into two

sections

10 and 11. Each of the

sections

10 and 11 is bounded by a flat or planar floor wall, a flat cover wall (both not illustrated) and by a

convex side wall

23 and 24 respectively, each possessing a radius of curvature r and by a

concave side wall

22 and 25 respectively, each possessing a radius of curvature R. In other words, these side walls possess the form of a cylindrical jacket with

axes

27 and 28 respectively disposed perpendicular to the plane of the drawing. The

side walls

22 and 23 of the section 10 are coaxially arranged with regard to one another, likewise the-

side walls

24 and 25 of the section 11. into one end 12 of the section 10 there opens an inlet opening 13 and from the one end I? n! the rim-tion 11 there merges an outlet opening 18. Both of the rcmaining ends 14 and 16 of the

sections

10 and 11 are in flow communication with one another by a throughflow or passage 15. The arrangement of the

sections

10 and 11 is mirror-image symmetrical with regard to the plane of symmetry indicated by the line 19.

Now in section 10 there is arranged a displacement vane 20 and in section 11 a displacement vane 21. The displacement vanes 20 and 21 each possess the shape of an arc of a cylindrical jacket, which spans an angle of about 270, and if there is neglected the wall thickness, possesses a diameter of R-l-r. As will be apparent from FIGS. 1 and 2 both of the

displacement vanes

20 and 21 are arranged in offset relationship with one another through an angle of about Both of the

displacement vanes

20 and 21 are rigidly connected with one another by any suitable and therefore not particularly illustrated means, for instance a plate which is parallel to the plane of the drawing, and mounted in such a way that they carry out a circular movement in the direction of the arrow 33, wherein the diameter 26 of the rotatory movement (while neglecting the wall thickness of the displacement vane) amounts to Rr.

From FIGS. 1 and 2 it will be readily apparent that the rotary movement of the displacement vanes 20 and 21 is not impaired in any way since the width of the chamber or

compartment sections

10 and 11 also amounts to V, I

R-r. In the position depicted in FIG. 1 the displacement vane 20 contacts in sealing fashion the side wall 23 at the contact point 29, the side wall 22 in sealing fashion at the contact point 30, in other words at the inner and outer contact point. Consequently, there will be recognized that between the inlet 13 and the through-flow or passage 15 there is no direct con nection. On the other hand, the displacement vane 21 within the compartment section 11 only contacts its outer side wall 25 and specifically at the contact point 31. In this case there prevails a direct connection between the through-flow 15 and the outlet 18. While the displacement vane 20 in the illustrated position is effective in a conveying or driving manner respectively, this is not so for the displacement vane 21 in its illustrated momentary position, because there is no sealing action which prevails between the front or end portions of the ends of the displacement vane and the corresponding chamber walls. This is also without significance because the displacement vanes work in pairs and there is no position during the rotatory movement, owing to the arrangement realized, in which the inlet 13 is in direct flow connection with the outlet 18.

Now in FIG. 2 there is shown a position in which the displacement vanes 20 and 21 have revolved further through about 90 in the counterclockwise direction from the position depicted in FIG. 1. The inner" contact point 29 between the displacement vane 20 and the wall 23 has wandered downward about the axis 27 through an angle of about 90, whereas no contact point exists any longer between the vane 20 and the wall 22. In this case there is therefore realized a direct flow connection between the inlet 13 and the outlet 18. On the other hand, in the compartment or chamber section 11 the contact point 31 between the vane 21 and the wall 25 has wandered upwards in the counterclockwise direction through 90 and at the same time there is obtained a new inner contact point 32 between the vane 21 and the wall 24. Consequently, the vnnr 2! in "NW effective in n conveying or driving man ner respectively.

Although it is obviously possible to design a practical exemplary embodiment constructionally in the manner depicted schematically in FIGS. 1 and 2, the illustration is provided especially for facilitating the description of the mode of operation of the proposed displacement machine.

A further exemplary embodiment of displacement machine has been illustrated in FIGS. 3 and 4, and which approximately corresponds to that shown in FIGS. 1 and 2 supplemented by the provision of a third displacement vane. There will be recognized in FIGS. 3 and 4 a displacement compartment or chamber 36 extending between an inlet 34 and an outlet 35. The displacement compartment 36 is subdivided into three circular ring sector-shaped

sections

37, 38 and 39 respectively, each extending through about 270. While the inlet 34 opens into the section 37 and the outlet extends from the end of the section 39, the remaining ends of such sections are connected via

throughpassages

40 and 41 with the ends of the central or middle section 38. Now a

respective displacement vane

42, 43 and 44 is arranged in the

sections

37, 38 and 39 respectively. The displacement vanes 42 to 44 are connected with one another also by not particularly shown means of any suitable design and mounted so as to be able to carry out a circulatory or revolving movement in the direction of the arrow 45. The geometric conditions concerning the width of the chamber or

compartment sections

37, 38 and 39, the radii of curvature of their side walls, and the diameter of the cylinder determined by the displacement vanes 42 to 44 are practically the same as already described in detail in conjunction with the discussion of FIGS. 1 and 2. With the exemplary embodiment depicted in FIGS. 3 and 4 the displacement vanes likewise cooperate with one another in pairs, namely the displacement vane 42 with the displacement vane 43 and the latter with the displacement vane 44. Each of the

displacement vanes

42, 43 and 44 is arranged in angularly offset relationship through about 90 with respect to the neighboring vane.

There will be recognized from the position illustrated in FIG. 3 that each

displacement vane

42, 43 and 44 has both an inner contact point as well as an outer contact point with the walls of the corresponding compartment or chamber section, namely the contact point 46 (inner) and 47 (outer) for the vane 42; contact point 48 (outer) and 49 (inner) for the vane 43 and contact point 50 (outer) and 51 (inner) for the vane 44. In this momentary position all three

vanes

42, 43 and 44 are effective in a conveying or driving sense respectively, depending upon the selected mode of operation of the machine, since each vane closes the throughflow or throughpassage in the corresponding chamber or compartment section.

In FIG. 4 there is illustrated a position in which the

displacement vanes

42, 43 and 44 are further angularly shifted or offset in the counterclockwise direction through about with regard to the showing of FIG. 3. Consequently, the inner and outer respective contact points 46, 51 and 47, of the

vanes

42 and 44 have wandered further by a corresponding angular magnitude, whereas in the case of the vane 43 there has disappeared the inner contact point 49 and there is only present the outer contact point 48. Consequently, between the throughflow openings or throughpassages 40 and 41 there prevails an unobstructed flow connection via the chamber or compartment section 38, which only remains until the vanes 42 44 have revolved further through an additional 45. After this further 45 of circular movement the contact point 47 (outer) and 51 (inner) of the

vanes

42 and 44 disappear, whereas the end of the vane 43 which is located at the bottom of FIG. 4 comes into sealing contact with the inner side wall of the chamber section 38.

Whereas the exemplary embodiment of FIGS. 3 and 4 to a certain extent can be designated as a series connection of three successive compartment or chamber sections, there is realized a parallel circuit configuration with the four chamber sections provided for the exemplary embodiment of FIG. 5, wherein in each case two series connected chamber sections in principle correspond to two parallel connected exemplary embodiments of FIGS. 1 and 2.

There will be recognized in FIG. 5 a chamber section 53 of the compartment, which chamber section is substantially circular ring-sector shaped and extends over about 270 and from an inlet opening 52, which should be imagined as constituting an extension which is perpendicular to the plane of the drawing and extending in the direction of the observer. Fromthis chamber section there extends a further likewise circular ring sector-shaped chamber section 55 which spans about 270 and which, in turn, opens into an outlet 56 which is to be imagined as extending perpendicular to the plane of the drawing but away from the observer instead of towards the observer as above.

At the right of FIG. 5 there extends from a further inlet opening 57, which likewise should be imagined as extending perpendicular to the plane of the drawing and towards the observer, a further circular ring sectorshaped chamber section 58 which spans an angle of about 270, and this further circular ring-shaped sector chamber section 58 also opens into an intermediate section 54. Extending from the intermediate section 54 is a fourth chamber section 59 which again has the shape of a circular ring-shaped sector which spans through about 270 and leads to a further outlet 60 which is to be imagined as perpendicular to the plane of the drawing and extending away from the observer.

The

inlet openings

52 and 57 are in flow communication with one another by a throughpassage (not shown) and lead to the inlet of the machine. In similar fashion the

outlets

56, 60 are in flow communication with one another and lead to the outlet of the machine.

In each of the

chamber sections

53, 55, 58 and 59 there is arranged a

respective displacement vane

61, 62, 63 and 64. Each of these displacement vanes is of similar design as the displacement: vanes of FIGS. 1 and 2 and FIGS. 3 and 4 respectively, and is angularly rotated or offset with regard to the neighboring vane by 90. The displacement vanes 61-64 are rigidly connected with one another by means of a carrier or support structure which has only been schematically indicated by reference character 65 and mounted in such a way that they conjointly carry out a circulatory or rotatory movement in the direction of the arrow 66 i.e., the counterclockwise direction.

In the position depicted in FIG. 5 the

displacement vanes

61 and 64 have the following sealing contact points with the walls of the

corresponding chamber sections

53, 55, 58 and 59: the displacement vanes 61 an outer contact point 67 and an inner contact point 68, the displacement vane 62 only an inner contact point 69, the displacement vane 63 both an inner contact point 70 and an outer" contact point 71, and

finally the displacement vane 64 only an outer contact point 72. From this it will be recognized that in the depicted position both

outlets

56, 68 are in unobstructive flow communication with the intermediate section 54 (similar to the situation of FIG. 1 as concerns the outlet 18 with the throughflow or throughpassage 15), whereas, on the other hand, no flow connection exists from the intermediate section 54 to the

inlets

52 and 57 respectively. Independent of the position in the revolving movement of the displacement vanes none of the

inlets

52, 57 is ever in obstructed flow communication with any one of the

outlets

56, 60.

Common to all of the embodiments of FIGS. 1 to is a throughflow free of pulsation, whether such be as operation as a motor or pump, and specifically without any change in volume, i.e., without any compression and expansion, which renders the disclosed displacement machine especially suitable for operation with liquid media.

In FIG. 6 there is illustrated an exemplary embodiment of the invention in which four displacement vanes with pairwise similar dimensions work in only two displacement chamber sections 75 and 77. The embodiment depicted in FIG. 6 possesses a displacement chamber 73 leading from an inlet 74 to a chamber section 75 in the form of a circular ring-shaped sector which spans an angle of 270. A connection or throughpassage section 76 merges with the section 75 and with such there again merges a circular ring sector-shaped section 77 which spans an angle of 270, and at which finally merges an outlet 78.

To this extent the construction is similar to the exemplary embodiment of FIGS. 1 and 2. The radius of curvature of the

convex side walls

79 and 81 of the chamber sections 75 and 77 is denoted by r and the radius of curvature of th concave side walls 80, 82 by R. In each of the chamber sections 75 and 77 there are only arranged two displacement vanes and specifically, a

respective displacement vane

83 and 85 of smaller diameter and a

respective displacement vane

84 and 86 of larger diameter.

All of these displacement vanes 83 86 are circular arc-shaped and span an angle of 270, and wherein those in the chamber section 75 are arranged in angularly offset or shifted relationship by 90 with respect to those in the chamber section 77.

The cylinder described by the

displacement vanes

83, 85 or so-called inner displacement vanes, possesses a diameter of 2r (R r)/2 (the wall thickness being considered to be negligible), the cylinder of the

displacement vanes

84 and 86 or the outer displacement vanes a diameter of 2R (R r)/2. The axes of the cylinder of the

inner displacement vanes

83 and 85 are designated by reference characters 88' and 90 respectively, those of the outer displacement vanes by 87 and 89 respectively. The arrangement is designed such that between the

axes

87 and 88 as well as between the

axes

89 and 90 there appears a respective distance or spacing of (R r)/2.

8 85. From this it will be recognized that the

outer displacement vanes

84 and 86 during their rotatory or revolving movement in the chamber sections and 77 respectively, only wipe or move across their peripheral region, if these chamber sections are imagined, by the broken indicated

lines

91 and 92, as being divided into a respective peripheral and a central region, whereas the smaller

inner displacement vanes

83,85 only wipe or move across the central region.

From this there is obtained, however, on the one hand, also the contact points of the displacement vanes with respect to one another, and with respect to the side walls of the chamber sections on the other hand.

With the position depicted in FIG. 6 the

displacement vanes

83 and 84 only contact one another at point 93, do not however contact the closer situated side walls 75 and 79, so that there exists an unobstructed flow communication between the inlet 74 and the intermediate section 76. On the other hand, both of the displacement vanes and 86 in the chamber section 77 possess the following contact points: the

vanes

85 and 86 contact one another at location 94, the larger outer vane 86 additionally contacts the concave side wall 82 at location 95, and the inner vane 85 contacts the convex side wall 81 at location 96. As a result, between the intermediate section 86 and the outlet 78, in the illustrated position, there is not present any unobstructed flow communication.

Since the respective contact points 93 and 94 between the

vanes

83 and 84 and 85 and 86 wander, during their revolving movement, along the

lines

91 and 92 respectively, there is realized during operation, basically no difference from the embodiment of FIGS. 1 and 2. With the same diameter of the revolving movement there is obtained, by doubling the number of displacement vanes and by their arrangement, practically a doubling of the conveying capacity or take-up capacity respectively. It is also possible to arrange in each of the chamber sections three displacement vanes, an inner, a central, and an outer vane respectively, wherein then the axes of the cylinder formed by the three vanes should be arranged through the corners of .an equilateral triangle with a side length of /2 3 (R r)3, whereas the revolving movement further possesses a diameter of (R r)/3 and the three displacement vanes revolve in the same sense, however with a phase displacement of or one-third of a revolution.

With all of the previously described dimensional relationships the wall thickness of the displacement vanes has been neglected. Therefore, as a practical matter during dimensioning of the inner width of a displacement chamber section there can be subtracted the amount of the wall thickness of the vane.

The exemplary embodiment depicted in FIG. 7 in exploded view, as concerns its mode of operation, corresponds to that of FIGS. 1 and 2. Therefore, it can be imagined that the embodiment of FIG. 7 has been realized from that of FIGS. 1 and 2 in that the embodiment of FIGS. 1 and 2 is divided along the line 19 into two halves and both thus resulting halves are displaced without rotation over one another until the

chamber sections

10 and 11 are located coaxially above one another.

The embodiment depicted in FIG. 7 will be seen to comprise two

housing halves

108 and 101 which sealing engage one another at the sealing surfaces 102 and 103. Both of the housing havles 100 and 101 enclose a displacement compartment or chamber within which revolves a one-piece displacement member 104 which purely for the sake of the illustration has been depicted in three parts.

The upper housing half 101 is designed to be practically the mirror symmetrical image of the lower housing half 100, and in the assembled condition is angularly shifted through 90 with respect to such and threaded thereon by means of bolts 105. It is therefore sufficient if only the lower housing half 100 is described, even if such only encompasses one-half of the displacement compartment or chamber. Leading into the displacement compartment is initially an inlet 106 which opens into a circular sector-shaped chamber section 107. The upper edge 108 of this chamber section 107 is located at a planar or flat sealing surface 109 which is rearwardly offset with respect to the sealing edge 102, as shown.

As already mentioned the displacement member or device 104 is constructed as a one-piece member and is only illustrated in its exploded condition in FIG. 7 for facilitating understanding. It possesses a first displacement vane 111, the height of which exactly corresponds to the depth of the chamber section 107 and is secured to the flat underside or bottom face of a first closure plate 112. In the mounted condition this flat underside sealingly bears upon the sealing surface 109. The closure plate 112 possesses a continuous bore or port 113, which in the mounted condition of the arrangement comes to bear upon the end region 110 of the chamber section 107. Additionally, there are formed at the corners of the closure plate 112 which is essentially square or quadratic, recesses 114 in the form of a quarter of a circle which, in the mounted condition, together with the bolts 105, ensure a guiding action for the displacement member or device 104 for its rotatory or revolving movement.

At the center of the closure plate 112 there is secured a hub body 115 with a bore 116 likewise extending through the closure plate 112. Upon the hub body 115 (in the mounted condition) there is secured a second closure plate 117 with a continuous bore 118 and a further non-visible bore which is in alignment with the bore 116. This closure plate 117 is constructed practically identical to the closure plate 114 and is only mounted in angularly shifted or rotated position through 90 relative thereto. A second displacement vane 119 is mounted upon a flat top surface or face of the closure plate 117, the displacement vane 119 being identical to the displacement vane 111 but mounted in angularly offset relationship through 90 with respect thereto.

Since, as already mentioned, the upper housing half 101 is mirror-image symmetrical to the lower housing half 100 and is shifted angularly with regard thereto through an angle of 90 the displacement vane 119 is effective at the upper housing half at the displacement chamber section.

If there is imagined that a phantom line depicted crankshaft 122 offset once in its lengthwise direction, as shown, extends through the components of the assembled machine, namely through the continuous central bore 120 and the lower housing half 100, through the bore 116 of the displacement device 104 and through the continuous central bore 121 of the upper housing half, then the following will be recognized: the

machine possesses two circular ring sector-shaped displacement chamber sections (each at the upper and the I lower housing half) which extend through about 270. In the chamber sections there revolves a respective displacement vane which is of circular sector-shaped and spans an angle of 270. The chamber sections and the displacement vanes are angularly offset through about with respect to one another. In one end of the one chamber section 107 there opens the inlet 106 of the machine, from one end of the other chamber section (in the upper housing half 101 at the side facing away from the observer) there emanates the machine outlet, whereas the other ends of the chamber sections are in flow communication with one another via the

bores

113 and 118 as well as the intermediate space between the

closure plates

112 and 117..

The embodiment illustrated by way of example in FIG. 7 can be referred to as a two storey or two tier arrangement and offers the advantage that both

displacement vanes

111, 119 can be practically directly driven from one and the same crankshaft.

Just as it was possible to modify the basic construction of FIGS. 1 and 2 to attain the practical exemplary embodiment of FIG. 7, it is also possible to modify the exemplary embodiments of FIGS. 3 and 4 into a three tier arrangement and that of FIG. 5 into a four tier arrangement each having only one crankshaft.

The same is also possible for the embodiment of FIG. 6, wherein however a double offset crankshaft and a total of four closure plates (a lowermost, two central and an uppermost closure plate). would be necessary for the four displacement vanes. While there is shown and described present preferred embodiments of the invention it is to be distinctly understood that the invention is not limited thereto, but may be otherwise variously embodied and practiced within the scope of the following claims. ACCORDINGLY,

What is claimed is:

1. A displacement machine comprising: a displacement chamber subdivided into at least two series connected consecutively arranged chamber sections, each of said chamber sections being bounded by an outer and inner substantially cylindrical jacket sector and by two substantially planar closure surfaces, a displacevment device arranged for carrying out a revolving movement and having a respective substantially cylindrical sector-shaped vane located in each of the chamber sections of the displacement chamber, each of said vanes having longitudinal edges. and curved surfaces, each of said vanes, independently of its momentary position during the course of said revolving movement, contacting by means of said longitudinal edges said planar closure surfaces and at least with one of its curved surfaces of the associated cylindrical jacket sector of the associated chamber section along a contact line, each of the chamber sections of the displacement chamber and each of the vanes of the displacement device spanning an angle of at least 270, a chamber section and the therein arranged vane being angularly shifted with respect to the connected chamber section and its respective vane by the complement of the span angle for 360, means for dividing said displacement chamber into four sections, and a common intermediate section for parallel connecting in pairs said four sections.

2. A displacement machine comprising: a displacement chamber subdivided into at least two series connected consecutively arranged chamber sections, each of said chamber sections including an inlet and an outlet end, connecting passage means for connecting the outlet end of one chamber section with the inlet end of the other chamber section, each of said chamber sections being bounded by an outer and an inner substantially cylindrical jacket sector and by two substantially planar closure surfaces, a displacement device arranged for carrying out a unidirectional revolving movement and having a respective substantially cylindrical sector-shaped vane located in each of the chamber sections of the displacement chamber with the displacement of each vane being confined to its associated chamber, each of said vanes having longitudinal edges and curved surfaces, each of said vanes, independently of its momentary position during the course of said unidirectional revolving movement, contacting by means of said longitudinal edges said planar closure surfaces and at least with one of its curved surfaces the associated cylindrical jacket sector of the associated chamber section along a contact line, each of the chamber sections of the displacement chamber and each of the vanes of the displacement device spanning an angle of at least 270, and a chamber section and the therein arranged vane is angularly shifted with respect to the connected chamber section and its respective vane by the complement of said span angle for 360.

3. The displacement machine as defined in claim 2, wherein the vanes constitute vane pairs which are substantially identical to one another.

4. The displacement machine as defined in claim 1,

wherein in each of the chamber sections of the displacement chamber there is arranged a number of said vanes, wherein the vanes in two successive sections pairwise correspond to one another with respect to their dimensions and wherein the diameter of the revolving movement corresponds to the inner width of the chamber section divided by the number of vanes per section, and wherein the displacement vanes with a phase displacement of 2 7T divided by the number of vanes per section revolve in the same sense.

5. The displacement machine as defined in claim 2, further including means for dividing the displacement chamber into the same number of chamber sections as there are present vanes.

6. The displacement machine as defined in claim 1, wherein the vanes are arranged coaxially with respect to one another,

7. The displacement machine as defined in claim 5, wherein the vanes constitute vane pairs which are substantially identical to one another, and wherein there are provided three of said vanes, each of which spans an angle of about 270, and each of which is arranged in a respective one of three consecutively arranged chamber sections of the displacement compartment.

8. The displacement machine as defined in claim 6, wherein the displacement device is designed as a onepiece component, means for arranging said vanes at an axial spacing from one another, said spacing serving to interconnect the chamber sections of the displacement chamber.

Claims

1. A displacement machine comprising: a displacement chamber subdivided into at least two series connected consecutively arranged chamber sections, each of said chamber sections being bounded by an outer and inner substantially cylindrical jacket sector and by two substantially planar closure surfaces, a displacement device arranged for carrying out a revolving movement and having a respective substantially cylindrical sector-shaped vane located in each of the chamber sections of the displacement chamber, each of said vanes having longitudinal edges and curved surfaces, each of said vanes, independently of its momentary position during the course of said revolving movement, contacting by means of said longitudinal edges said planar closure surfaces and at least with one of its curved surfaces of the associated cylindrical jacket sector of the associated chamber section along a contact line, each of the chamber sections of the displacement chamber and each of the vanes of the displacement device spanning an angle of at least 270*, a chamber section and the therein arranged vane being angularly shifted with respect to the connected chamber section and its respective vane by the complement of the span angle for 360*, means for dividing said displacement chamber into four sections, and a common intermediate section for parallel connecting in pairs said four sections.

2. A displacement machine comprising: a displacement chamber subdivided into at least two series connected consecutively arranged chamber sections, each of said chamber sections including an inlet and an outlet end, connecting passage means for connecting the outlet end of one chamber section with the inlet end of the other chamber section, each of said chamber sections being bounded by an outer and an inner substantially cylindrical jacket sector and by two substantially planar closure surfaces, a displacement device arranged for carrying out a unidirectional revolving movement and having a respective substantially cylindrical sector-shaped vane located in each of the chamber sections of the displacement chamber with the displacement of each vane being confined to its associated chamber, each of said vanes having longitudinal edges and curved surfaces, each of said vanes, independently of its momentary position during the course of said unidirectional revolving movement, contacting by means of said longitudinal edges said planar closure surfaces and at least with one of its curved surfaces the associated cylindrical jacket sector of the associated chamber section along a contact line, each of the chamber sections of the displacement chamber and each of the vanes of the displacement device spanning an angle of at least 270*, and a chamber section and the therein arranged vane is angularly shifted with respect to the connected chamber section and its respective vane by the complement of said span angle for 360*.

4. The displacement machine as defined in claim 1, wherein in each of the chamber sections of the displacement chamber there is arranged a number of said vanes, wherein the vanes in two successive sections pairwise correspond to one another with respect to their dimensions and wherein the diameter of the revolving movement corresponds to the inner width of the chamber section divided by the number of vanes per section, and wherein the displacement vanes with a phase displacement of 2 pi divided by the number of vanes per section revolve in the same sense.

6. The displacement machine as defined in claim 1, wherein the vanes are arranged coaxially with respect to one another.

7. The displacement machine as defined in claim 5, wherein the vanes constitute vane pairs which are substantially identical to one another, and wherein there are provided three of said vanes, each of which spans an angle of about 270*, and each of which is arranged in a respective one of three consecutively arranged chamber sections of the displacement compartment.

8. The displacement machine as defined in claim 6, wherein the displacement device is designed as a one-piece component, means for arranging said vanes at an axial spacing from one another, said spacing serving to interconnect the chamber sections of the displacement chamber.