DE2428228A1 - DEVICE FOR CONVEYING OR TREATING A FLUID - Google Patents

Description

Device for conveying or treating a fluid

The invention relates to "a device for conveying or treating of a fluid, in particular a device for compressing, expanding or pumping a fluid.

The requirements for gas compressors and expansion machines as well as for liquid pumps are well known and it are a number of different types of such devices. In these devices, the operating medium is through the Inlet sucked in and discharged through the outlet at a higher pressure. If it is an operating medium. a gas is, its volume can be reduced before it is discharged through the outlet, so that the device as a compressor works., If the operating medium is a pressurized gas is introduced into the device and this increases its volume j the device works as an expansion machine,

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can release the mechanical energy and, if necessary, generate cold. After all, a fluid can be at different Press, but are sucked in and released again without a significant change in volume, so that the device as a fluid pump serves.

In the following the device according to the invention for conveying a fluid and the corresponding known devices referred to as a compressor for reasons of convenience. It should be noted, however, that the device according to the invention can also be used as an expansion machine and as a pump and their use as such is different for the various Embodiments described.

It is not necessary to discuss the prior art in detail insofar as it relates to dynamic devices such as centrifugal compressors and pumps or, more generally, positive displacement devices that work with blades or gears other shape than Rotati ons are formed in front of directions. However, it is worth noting some features that make these species more well known Identify devices and can serve for a comparison with the fluid displacement device according to the invention.

Pumps, compressors and fans or blowers, which can be referred to as "dynamic" devices, must work at high speed in order to achieve a large pressure ratio and they usually have efficiencies of less than 90 %, based on the mechanical energy converted into flow and pressure energy Energy. Such dynamic devices are widely used in large designs such as, for example, gas turbine compressors, stationary steam turbines for power plants and the like.

Pumps or compressors of the positive displacement type, which are equipped with blades, have sliding velocities which the; Radius of the blades are proportional, with the sliding action ^! takes place with changing angles on the blades. aside from that

40 & 881 / 1Ό12 "~" ³ "

the blades work in a casing of certain axial Length, so that any wear on their flat end faces an enlargement of the gap and thus an increase in the Blowing through or the leakage of the device brings with it. Centrifugal pumps and compressors of the positive displacement type are designed in such a way that that the revolving elements are movable between plates or side surfaces, so that to reduce the blow-through with unhindered rotational movement at the same time, tight tolerances must be provided «A wear and tear between the rotating Components and the side surfaces leads to stronger blowing, so that the distance between the side surfaces by means of screws and very precisely designed seals in the form of washers must be adjusted. The seals in turn can corrosive fluids or fluids at extreme temperatures, z. B. very cold liquids or hot gases, not withstand. In addition, these seals must be very precisely arranged Have edges so that the rotating blades are not damaged, thereby further assembling the device is made more difficult.

In most industrial areas, especially large-scale plants, Fluxdpurspen and compressors are used that correspond to the respective requirements. Nevertheless, there remains a need for simple, high-efficiency devices that essentially unaffected by wear and tear and for a wide range of fluids and over a wide range of Operating conditions can be used to make them work as a pump, compressor or expansion machine. The inventive Device that meets these requirements is based on the use of spiral-shaped elements with enveloping surfaces, which have changing points of contact so that they are. , moving, closed volumes, known as pockets which carry the operating medium with them. The points of contact that these pockets form and between the spiral elements are twofold Type, line contacts between the cylindrical surfaces of the spiral-shaped elements and surface contacts between planes

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Surfaces. The volume of such a closed pocket changes as it moves. At some point it is at least one such sealed pocket is present.

One type of device is known, commonly referred to as scroll pumps, compressors and machines, in which two interlocking helical or involute elements of equal pitch are mounted on separate side surfaces. These spirals are offset from one another at an angle and radially in such a way that they lie against one another along at least two contact lines such as are present between surfaces that are curved in the shape of a spiral. Two lines of contact lie approximately on a radius, starting from the central area of the spiral elements. The fluid volume formed in this way therefore extends completely around the central. area of the spiral elements. In certain special cases, the pocket or the fluid volume does not extend entirely over 360 °, but rather, because of a special opening control, it extends over a smaller angle from the central region of the spiral elements. The pockets form volumes of fluid the angular position of which changes with the relative trajectory of the spiral centers, with all pockets maintaining the same relative angular position. As the contact lines move along the spiral surfaces, the pockets formed in this way experience a change in volume. The resulting zones of lowest and highest pressure are connected to fluid openings.

Such a device is described in the early US-PS 801 182. j Other patents dealing with compressors and pumps _; dealing with spiral elements are the US patent _; Writings 1 376 291, 2 809 779, 2 841 089, 3 560 119 and 3 600 114 as well as GB-PS 486 192.

Although a device with spiral-shaped elements is long; was known and recognized to have certain advantages * has, this known device has not in practice '

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enforce, especially because of the problems of sealing

j, the wear and, to a certain extent, dsr sin and outlet control, which resulted in considerable limitations in terms of efficiency, service life and the achievable pressure ratio. In some of the known devices, the components must be machined in such a way that they have precisely defined shapes _P the components being used with very small tolerances in order to keep the axial sealing gaps sufficiently small so that a usable pressure ratio is obtained. This is difficult to do and corresponds to the difficulty of building a reciprocating piston device without the use of piston rings. In other known devices, the radial seal is formed by more than one radial restriction of freedom of movement, each being achieved by separate components, so that precise compensation is necessary to achieve an effective radial seal. If during extended operation of such a device this; Compensation by one of the components which is subject to greater wear or is disturbed by some other mechanism, the problem of wear on the other components increases until a satisfactory radial seal can no longer be maintained.

Instead of bores for withdrawing the compressed fluid, in a number of known devices with spiral elements helical passages have been provided, the pressure: ratio formerly being approximately the ratio of the radius of the outermost pocket to the radius of the innermost pocket at the moment of the start of the fluid discharge, ie at the moment of '. Opening of the inner pocket, was limited. When designing the known devices with spiral elements it was' · therefore greater to achieve a pressure ratio than about | two essentials is to design the spiral elements and the side plates or side surfaces so that they are in a very large ^,! - resembled flat pancakes. In contrast, the he j

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inventive device with spiral elements features, by means of which the outer diameter of the spiral elements can be reduced while obtaining the desired pressure ratios. One of these features are arch elements that are designed to allow the fluid to flow into the device as well control the outflow of the fluid therefrom.

The resulting solutions of the sealing, the wear and the arrangement of the openings by these and other attempts were not sufficient. Thus, in the known devices, the advantages of a device with spiral elements (Simplicity, high efficiency, elasticity, reversibility and the like) have not been achieved and they have usually been through nullified the difficulties of sealing, wear and control of the openings. It would therefore be desirable To be able to build fluid displacement devices with spiral elements, in which the advantages of this type of device can be exploited and in which there are practically no problems with regard to sealing or wear and the arrangement or control of openings occur as indicated above.

The invention should therefore one that can improved for practical and useful type fluid displacement apparatus are provided for operating by spiral elements as a compressor, expander or pump, v / ffective axial and _radial: said seal over extended periods of operation, simple in construction and is relatively cheap, has relatively few moving parts and a limited number of sliding surfaces and ^: which is subject to less friction and less wear; than other devices of this type that serve the same purpose ^! were laid out. Furthermore, such a device should be designed in such a way that the wear essentially compensates for itself. '.

As a compressor or expansion machine, the inventive j Apparatus for treating a wide variety of fluids;

be suitable over a wide temperature range. i

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Furthermore, according to the invention, such a device should be designed so that it is particularly suitable for large output sizes and for systems in which the driving forces are indicative of the spiral elements.

According to the invention, a device of this type is provided which is compliant in the radial direction and has orbital motion of the spiral element allows this to move inwards and outwards relative to the machine axis depending on the original relocation of the components or the gradual wear and tear or to compensate that does not occur at times compressible material, like a mass of liquid Wear residues or sucked-in dirt can.

The device provided with spiral elements according to the invention has a drive device which allows a reduction of the radial restrictions within the device to only those which are present by the moving contact lines between the surfaces of the arc elements forming the fluid pockets. This drive device has a device which counteracts the total centrifugal force on the moving scroll element or a fraction of this centrifugal force with an inwardly directed radial (centripetal) force. Thus, a touch, that is, radial sealing force causing present, returns the • s wear to a minimum, regardless of the operation of other device components such as the ^input: is the direction which maintains the desired angular relationship between the spiral elements and the axial sealing means . The axial seal is preferably formed by pressurized fluid withdrawn from the zone of highest pressure and a spring exerting a force on one of the spiral elements to urge it against the other spiral element.

4 09881/1012 ^r

One embodiment of the device according to the invention has a spiral driver as the drive device, which is driven by Bearing is mounted on the main drive shaft while the moving scroll element is free to move in the axial direction, so that it can respond to the fluid pressure acting on its outer surface to achieve an axial seal. Of the Spiral driver causes a path movement of the spiral element by creating a rolling contact line between its cylindrical surface and a drive surface is made on the movable scroll member. By the Orbit radius of the spiral driver is kept smaller than the orbit radius of the movable scroll element the required opposing centripetal force is formed in the drive device.

In another embodiment of the device according to the invention is a mechanical connection device which is flexible in the radial direction between the one describing a path Spiral element and its drive device are provided. Such a mechanical connecting device which is flexible in the radial direction can generate a centripetal force that counteracts part of the centrifugal force, so that part the centrifugal force is available to achieve a controlled radial seal. In this embodiment v / eist the resilient mechanical connection device on mechanical springs which counteract part of the centrifugal force.

In a further embodiment, they are separate from the mechanical connecting device which is flexible in the radial direction Facilities, e.g. B. counterweights are provided, which compensate for all or almost all of the centrifugal force, which acts on the spiral element describing a path, the connecting devices which are flexible in the radial direction, z. B. mechanical springs, ensure the necessary radial sealing forces. In this embodiment, the radial Sealing force of pressure changes at the inlet and outlet of the machine

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_ 9 -

and made independent of changes in operating speed four den.

The spiral elements are arranged at an angle to one another by means of a coupling with sliding friction or rolling elements. the A connecting device which is flexible in the radial direction can be a sliding connection or a pivoting connection. Either a spiral element, or both, can be cooled and optionally the contact surfaces can be lubricated.

For better control of the fluid flowing in and out, if necessary, openings provided with valves can be provided in the fluid displacement device according to the invention. Valve-controlled orifices are generally not required for liquid pumps or for gas compressors and expansion machines where the pressure ratios are small or where a "pancake" geometric configuration is possible. In order to achieve various desired properties such as different pressure ratios, control of the fluid volume, time of discharge, overall size of the device and the like, different designs of the spiral elements can be used in a wide range. The device according to the invention is easily reversible from a compressor to an expansion machine and it can be used for a large number of fluids as the operating medium via a _; wide temperature range can be used. Many of the illustrated embodiments can also be used as liquid pumps.

For example, embodiments according to the invention are; explained in more detail below with reference to the drawings, in which

Fig. 1 to 4 schematically, for. B. spiral arch elements j show one of which, relative to the other, is in a circular; orbit, explaining the manner in which a device with such spiral elements compresses a gas can.

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Fig. 5 shows a plan view in connection with two side views a spiral element indicating the main forces to which this spiral-shaped part is exposed.

FIGS. 6A and 6B schematically explain the forces in FIG Radial-tangential plane acting on a spiral element, showing the mechanism by which the radial Sealing forces are generated.

Figure 7 is a cross-sectional view of the scroll driver with the movable and stationary scroll members of the type and show the manner in which the axial seal is achieved.

FIG. 8 is a cross-sectional view of the compressor of FIG. 7.

9 is a partially cut-away side view of a portion of another embodiment of a compressor according to the invention.

FIG. 10 shows a section through the compressor according to FIG. 9 along the line 10-10 in FIG. 9.

11 and 12 are a plan view and a cross-sectional view of another embodiment, a coupling element, as found in the compressor of FIGS. 9 and 10 use.

Fig. 13 shows a cross section through the spiral elements of an embodiment of a compressor according to the invention, wherein the arch elements are designed so that the compression space at the beginning of the delivery of compressed gas by a central opening is controlled so that one can have an intermittent Receives opening control.

FIG. 14 is a cross section taken along line 14-14 in FIG. 13.

Fig. 15 shows a cross section through a compressor according to the invention, in which the spiral elements around parallel Rotate axes.

FIG. 16 is a cross-sectional view of the driving scroll element of FIG. 15 taken along line 16-16 in FIG. 15.

17 shows a longitudinal section of a compressor according to the invention, which has a coupling with sliding friction, a pivot connection and springs for balancing part of the centrifugal

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having force acting on the spiral element moving on a path.

Fig. 18 is a partial section through the fixed scroll member, wherein in detail one embodiment of a Device is shown which generates an axial sealing force.

Figure 19 shows an end view of the fixed scroll member with the back or outside of the side plate and showing the arrangement of cooling channels formed in the side plate.

Fig. 20 shows an end view of a portion of the front or inside of the side plate of the stationary Spiral element, the lubrication groove in the end face of the arch element and the introduction of a lubricant in this groove is shown.

Figure 21 is a cross section taken along line 21-21 in Figure 20 showing the inlet conduit for the lubricant.

Figure 22 is a cross section taken along line 22-22 in Figure 17 through the helical arch members.

Figure 23 shows, in an end view, part of the front or outside of the side panel of the web moving spiral element, wherein a coupling wedge is shown.

Figure 24 is a top plan view of one embodiment of a coupling element.

FIG. 25 shows a cross section through the coupling element according to FIG. 24 along the line 25-25 of this figure.

Fig. 26 is a cross-section through the coupling element taken along line 26-26 in Fig. 24.;

Fig. 27 shows a view of the inner surface of a housing part, with the coupling wedges and the lubricant ■ channels are shown.

FIG. 28 shows a cross section along the line 28-28 through the rear side of the housing according to FIG. 27.

Fig. 29 shows a view of another embodiment of a coupling element which is attached to the housing part and the spiral element describing a path is applied via ¥ älzkörper.

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FIG. 30 shows, in a partial section, the spiral element between the housing part and the spiral element describing a path arranged coupling element.

31 is a view of a pivot link; that as a resilient mechanical connecting device between the spiral element describing a path and the drive device are used.

FIG. 32 explains a modification of the pivot connection according to FIG. 31.

33-35 are sectional, end and side views of a slider assembly shown as resilient mechanical connecting means between the spiral element describing a path and the drive means serves.

Fig. 36 is a cross-section through the main drive shaft taken along line 36-36 in Fig. 17 showing the shape of the counterweights for balancing the centrifugal force ^; is intended to eliminate vibrations.

Before special embodiments of the device according to the invention will first be described briefly in general the basic mode of operation of a spiral element provided device are explained so that it is clear in which way the fluid displacement is achieved. In the Operation of this device is a sealed fluid pocket moved from one area to another area, which may have a different pressure. When the fluid is compressed as it is moved from the low to the higher pressure area, the device serves as a compressor. In a direction of movement from the area of higher pressure to an area of lower pressure, it serves as an expansion machine and when the volume of fluid remains substantially constant regardless of pressure, the device serves as a pump. :

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The sealed fluid pocket is created by two parallel planes on the side plates and bounded by two cylindrical surfaces formed by the involute of a circle or some other suitable curved shape can be formed. The spiral elements have parallel axes, since only in this way the continuous tight contact between the flat surfaces of the spiral elements can be maintained. Between these parallel planes moves the sealed pocket, while the two lines of contact between the cylindrical surfaces be moved further. These lines of contact continue to move because a cylindrical element, e.g. B. a spiral element, rolls over the other. This is achieved, for example, in that a spiral element remains fixed while the other describes a path. In the following detailed description, it is for the sake of simplicity assumed that the fluid displacement device is a compressor and that one of the scroll elements is fixedly arranged during the other describes a circular path.

1 to 4 are schematic views of a compressor with the side plates removed and only the spiral arcuate elements of the spiral elements shown. In the following description, the term "spiral member" is used to denote the component, which consists of the two side plates and the elements which is advanced, the contact surfaces with ^the: form moving contact lines. The term "arch element" is used to refer to those elements which make up the moving lines of contact. These arch elements have the form Z ₀ B _{0 of} an involute of a circle (involute spiral) _{f of} a! Circular arc and the like, and they have both a height and a thickness dimension. The thickness can vary over the; Change the arc length of the arc element. ';

I In Figures "1 to 4" form a fixed spiral element: with the arch element 10 in the form of an involute spiral with the axis 11 and a movable spiral element with the Arch element 12 in the form of another involute spiral

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of the same pitch as the spiral 10 and with the axis 13 the components which form the displaceable, sealed fluid pocket 14, which is hatched to simplify the illustration. The involute spirals 10 and 12 can be produced, for example, in that a thread is looped around a reference circle with the radius R. The distance between corresponding points of adjacent arcuate elements of each spiral is equal to the circumference of the generating circle. This distance between corresponding points of adjacent arcuate elements of a spiral element is also equal to the pitch P. As FIG. 1 shows, the two spiral elements can touch at several points, e.g. B. in Fig. 1 at points A, B, C and D. These points represent the lines of contact between the cylindrical surfaces indicated above. The lines of contact C and D in Fig. 1 delimit the hatched pocket 14. These lines of contact are approximately on a single radius passing through point 11 to form a pocket 14 which extends approximately once around the central portion of the spiral elements. Since the spiral arcuate elements have a height dimension (normal to the plane of the drawing), the pocket forms a fluid volume which becomes smaller from FIG. 1 to FIG. 4, while the movable spiral element rotates around a circle 15 with the radius (P / 2) -t moved, where t is the thickness of the arch element. Since the arch element 12 does not rotate while it describes its path, the path described by the walls of the arch element 12 can still be represented as a circle 16. As indicated in FIGS. 1 to 4, the sheet member 10 has a shape congruent with two Evolventenspiralen features 17 and 18 marked] while the sheet member 12, a j by two congruent Evolventenspiralen. 19 and 20 has a certain shape. : In this embodiment, spiral-shaped sheet members I, the congruence results from the fact that a spiral form by doing sine simple rotation of 180 ° or less about its axis \ with the other spiral shape can be made congruent ;, connected to a slight displacement, so that the '' W ttelpunkte coincide. The thickness t of the spiral,

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Arch elements are shown as identical, although this is is not necessary. As will be explained below, the arch elements can have a wide variety of shapes and sizes extend around their axis different times.

The side plate, not shown in FIGS. 1 to 4, to which the stationary arch element 10 is attached has an opening 21 for high pressure _{fluid (} and as the movable arch element 12 moves along a path, the fluid pocket 14 is counterclockwise to be removed In Fig. 3 , the volume of fluid is in communication with the opening 21 so that the high pressure fluid can flow out. The flow of the high pressure fluid continues, as shown in Fig. 4, until the movable arch element changes its path has described circle 15 and a new volume of fluid is sealed for compression and transfer, as shown in FIG.

When a high pressure fluid is introduced through port 21, so the movable arch element 12 is driven so that it describes a path in a clockwise direction under the force of the fluid pressure, where it gives off mechanical energy in the form of a rotary motion while the fluid pockets are under magnification expand the volume. In such an arrangement, the apparatus is an expansion machine and it may, if necessary can be used to generate cold.

Although this principle of operation with a spiral element _; menten-equipped device was known for a long time, as was the state ^! : the technology shows, a practically usable machine, which would have justified the use of such devices on an economic scale, could not be completed so far. This is due, at least in part, to the difficulties of sealing and wear. In particular, the known devices do not have an effective combination of a continuous axial and radial seal and it was tried in many cases, the freedom of movement of the spiral elements by a

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mechanism other than the lines of contact of the arch elements themselves in the radial direction to "restrict, such mechanisms were also used to control the angular phase relationships between the scroll elements. By lack of continuous axial and radial sealing can blow through occur, which can reduce the efficiency of the device so that the operation is no longer economical. The restriction of radial freedom of movement by devices other than the lines of contact of the arch elements on the spiral elements possibly leads to wear of the surfaces lying against one another and thus to leakage. In general such wear will change from surface to surface and not self-compensate, so that it only exacerbates the wear problem with prolonged use. A combination of mechanisms for achieving a desired angular phase relationship between the spiral elements with such a device for restricting the Radial freedom of movement can increase the wear problem, making prolonged operation impossible.

For a better understanding of the difficulty of sealing: a provided with scroll members device and for ^ER: purification of the mechanism is achieved by the axial and radial sealing with the inventive device, it appears appropriate to examine the main axial and radial forces which act on a spiral element. The total external axial force on a pair of spiral elements is the sum of a contact sealing force that acts between flat surfaces and the internal gas charge. Therefore, if an external force is provided which is always greater than the axial force exerted by the enclosed gas, an axial seal can be achieved.

While the axial seal is required, the end faces of the arch element edges against the side plate of the opposite spiral element to seal, the radial 'seal is necessary to achieve a sealing effect along the

A0 9881/1 012 - 17 -

To maintain lines of contact created by the cylindrical surfaces of the arch elements on the spiral elements while the one spiral element moves on its path (see, for example, locations A, B, C and D in Figs show the displacement of these lines of contact). The main forces that determine the radial sealing of the spiral elements include tangential forces based on the reaction of the fluid within the spiral volume, which is achieved by mechanical limitation in the radial direction and centrifugal forces due to the movement of one spiral element along its path. In addition to these forces generated by the device, other external forces _; be applied.

According to a first embodiment of the invention, the disadvantages associated with the known devices thereby eliminated or reduced to a minimum that the restrictions the radial displacement movement can only be limited to those caused by the contact lines of the arch elements occur even by providing a driving force to the movable scroll member, the one inward directed radial component having at least one Part of the centrifugal force acting on the movable scroll element is counteracted, and by a coupling device to control the angular phase ratio of the two; the spiral elements is provided, which is independent of a a constraint inducing device is operating. The ar-. Both of the device remains independent of any Changes in pressure within the spiral elements. The wear and tear on the lines of contact between the arch elements on the Spiral elements essentially compensate for themselves, so that; A permanent effective radial over long periods of operation Sealing is in place. The axial sealing is preferably achieved by using gas from the area of highest pressure in: Connection to a suitably preloaded spring '; reached, which the spiral elements continuously in the axial direction; pushing each other.

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In the following, the main axial and radial forces that act on a spiral element will be explained to explain the axial and radial sealing. As FIG. 5 shows, the total external force F ″ acting in the axial direction on a pair of spiral elements is the sum of the sealing force caused by the contact of the involute and the gas charge. If an external force is therefore provided which is always greater than the force exerted in the axial direction by the enclosed gas, an axial seal can be achieved. In the device according to the invention, for this purpose, fluid is withdrawn from the area of the highest pressure and used to generate an axial sealing force which is essentially proportional to the highest pressure within the fluid pockets. According to FIG. 5, therefore, there must be an excess of axial force on the spiral element, which is directed along the arrow F,;

works. This excess force results in the sealing of the edges of one spiral element with respect to the other and it is counteracted by gas forces which are directed against the force F _e indicated in FIG.

Fig. 7 illustrates an example embodiment of a device in which a permanent axial seal by the use of gas withdrawn from the area of highest pressure is achieved, aided by the use of a Spring, which presses the spiral elements against each other for tight contact in the axial direction. In the embodiment according to Figure 7, which shows a cross section through the spiral elements and a spiral driver, this spiral driver becomes together with a "floating" movable scroll element used to provide a permanent, self-adjusting axial seal to reach. The arch element 10 with the surfaces forming the lines of contact on the stationary spiral element, which is generally is indicated at 25, is made with a fixed side plate 26 in one piece or attached thereto. This side plate 26 ends on its peripheral edge in an annular housing 27 which has an annular sealing surface 28 having. The arch element 12 with the surfaces forming the lines of contact on the movable spiral element, the general

mine is designated 30, consists of one piece with a movable side plate 31 or is attached to this, wherein the sealing surface 32 is designed along the circumference of this side plate 31 so that it is on the annular sealing surface 28 of the stationary scroll member 25 so that the internal volume 33 formed between the side plates 26 and 31 in Axial direction is sealed. Between the sealing surfaces 28 and 32 there must be continuous and all-round frictional contact, even if these surfaces are subject to wear during operation. Furthermore, the axial sealing force is used to to press the side plates tightly against the end faces of the arch elements of the opposite spiral element 41 and 42, so that the fluid pockets are sealed at these contact surfaces. This required axial sealing is achieved by the Use of a spiral driver, generally designated 35, in conjunction with the movable spiral element 30 achieved that can swim or is mobile under the influence of the attacking forces. In other words, moved This spiral element 30 is under the influence of the acting forces until a sufficiently .proof system for sealing the pockets is reached.

In the embodiment according to FIG. 7, the movable spiral element 30 comprises a housing ring surrounding the spiral driver 36, which delimits a cylindrical space 37 in which the spiral driver 35 is arranged. Has on the inside this ring 36 perpendicular to the plane of the side plate 31 has a wall 38, an annular shoulder 39 and a pressurized one Sealing surface 40 which forms the central portion of the outer surface; of the movable scroll member 30. The spiral driver 35 is generally designed as a piston and it has in this embodiment a ring 45 with an inner annular shoulder 46 for the installation of a bearing 47 and in the middle a closure disk 48, the outside 49 | the drive surface 40 is opposite. The ring. 45 of the spiral driver has a diameter D ,, which is slightly smaller than the diameter D_ of the inner wall 38, so that there is an annular gap

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50 results. The difference in diameter can be expressed as (Eg-Ej) / D and it can range from about 0.001 to about 0.2. The ring 45 is designed so that it has a circumferential groove 51 for receiving an elastomeric sealing ring which lies between the spiral driver and the inner wall 38 of the housing ring 36 for the spiral driver. With a spring 53 is referred to, which then exerts an axial force on the movable spiral element when the pressure supplied and thus the force of the gas charge is zero. This pretensioned spring 53 is arranged so that it rests against the annular shoulder 39 and on the circumference of the disk 48 of the spiral driver, whereby a flat, axially sealed fluid volume 54 is formed between the disk 48 of the spiral driver and the drive surface 40 of the movable spiral element . Certain devices, such as, for example, the recess 44 in the spring 53, must be provided so that the spring does not accidentally seal off the space 37 from the space 54, because these volumes must be permanently in fluid connection with one another. A bore 55 establishes a connection between the area of the highest fluid pressure in the space 33 and the sealed space 54. The spiral driver 35 is attached to a drive shaft 56 via a bearing 47. The mechanism by which the movable scroll member 30 is driven will be explained below.

As far as the movable spiral element 30 is not rigidly connected to the spiral driver, it can move in the axial direction move freely, d. H. it is floating. By introducing high pressure fluid through bore 55 in the sealed space 54 is a force F- which is essentially

borrowed equal to the force exerted by the gas inside, provided as an axial sealing force, provided that the area of the force exerting surface of the spiral driver is sufficiently large. The fluid pressure in the sealed space 54 pushes the movable spiral element away from the spiral follower and against the fixed spiral element _s | so that the surfaces 28 and 32 are close together and also between the edges of the arch elements and the side

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plates of the spiral elements a tight system is achieved. When these sealing surfaces wear out, the system becomes airtight still maintained because the movable scroll member yields under the force of the fluid pressure in the sealed space 54 or can adjust. In practice it is advisable to interpret the total force F by means of the spring 53 in such a way that

el

that F does not become zero even if the pressure difference in a

the system should become zero. The spring 53 thus ensures

an axial sealing force at start-up and for a certain; additional axial sealing force during operation.

While the axial seal is required for the tight abutment of the end faces of the arch element edges with the side plate of the opposite spiral element, a tight abutment must be maintained with the radial seal along the lines of contact that occur through the cylindrical 'surfaces of the arch elements on the spiral elements, while the movable spiral element describes its path (cf. e.g. the contact points A, B, C and D in FIGS. 1 · to 4, which show the displacement of these contact lines) .: The main forces which determine the radial sealing of the spiral elements , are shown in Fig. 5 in simplified form \ , the forces on the movable scroll element; with a single arch member 12a attached to a side plate 31a. While the spiral element is a trajectory. describes with the radius R__, it is subject to a tangential: force F ₊ and perpendicular to it a contact force which the centri- '

2
fugalkraft mkjR, where m is the mass of the spiral element ^: and ω is its angular velocity. This centrifugal force exceeds 3ene, which is necessary to achieve a sufficient radial seal, and the size of this excess centrifugal force determines the extent of the wear to which the; are subject to adjacent, cylindrical surfaces of the arch elements. In the device according to this embodiment, the spiral element describing a path has trains- _>; arranged drive device on a device, which counteracts a part of the centrifugal force or is counter-directed, 'so that a contact force results that is sufficiently large, so that an effective an ^ iMilLale, sealing and at the same time. i

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- 22 -

does not receive excessive wear. The drive device. The device according to the invention thus has a device which _{generates a centripetal radial force F r} which counteracts part of the centrifugal force which acts on the movable spiral element. This is in direct [contrary to the teaching of the prior art, which proposes the use of an increased centrifugal force for obtaining a radial seal (see FIG. Z. B. GB-PS 486 192).

In practice, the actual proportion of the centrifugal force that is canceled by the centripetal radial force due to this device will depend on various factors; that can be related to each other. The optimal balance between the centrifugal force, which is never reduced to zero in the device according to FIGS. 7 and 8, and the ^; Centripetal force can thereby for a given device ^; be determined that these factors are taken into account, such as the specific field of application for which the device is used, the use or non-use of lubricants; average, the material of which the arch elements are made, I the operating speed, the desired service life of the device- ·; tung and the like. For a dry running compressor 'you will generally have a greater portion of the centrifugal force must balance than a compressor that works with \ a suitable lubricant, and a compressor with curved elements of a lighter-wearing: Material is to compensate for a larger part of the centrifugal force must be made of a material that is not subject to wear than a compressor with arch elements j. In general, higher operating speeds and longer | Lifetime that a larger part of the centrifugal force is canceled by a centripetal force. ;

In connection with the device for canceling part ί of the centrifugal force on the spiral element _f describing a path, the device according to the invention is characterized by further features which enable the contact force to be set so that the ralial sealing force between the spiral elements

409881/1012 - 23 -

is maintained continuously so that there is minimal wear and tear and minimal fluid leakage. One of those characteristics is the limitation of the radial restrictions on freedom of movement within the device to those in motion Lines of contact between the arch elements. This results in these radial limitations, which are caused solely by the one centripetal Power generating device are controlled, not only minimal wear, but give the device in Operation of such elasticity that a large part of the wear that occurs is automatically compensated for. The limitation the radial restrictions on freedom of movement on only the moving lines of contact between the arch elements is contrary to the teaching of the prior art, such as that in U.S. Patent 3,600,114 is reproduced.

Another important feature of the device according to the invention is the use of a coupling device that maintains a fixed angular relationship between the spiral elements, this device being separate and distinct from the drive device. By using such a Coupling device in connection with the specific drive device according to the invention and by limiting the radial Restrictions on freedom of movement on the moving

the lines of contact between the cylindrical surfaces i the arch elements can with the device according to the invention; at least to a very great extent the difficulties be overcome, which in the known devices j in terms of radial sealing and wear er! give. J

In the embodiments of the devices I according to the invention according to FIGS. 7 to 16, the drive device, which is a; centripetal force to cancel part of the centrifugal-> force generated so that the desired contact force and the radial; Sealing is achieved, for example, by a combination; a device for forming one of the movable scroll members associated, cylindrical driven surface and:

4 09 881/1012 - 24 -

a spiral driver formed, which has a driving cylin-; drical surface forms which the movable scroll element via a line of contact with the driven surface a path can be described. If you choose the radius R of the moving ■ Spiral element larger than the orbit radius R ^ of the spiral mit- j takers, one obtains the desired centripetal, inward; directed radial force, which is part of the centrifugal force counteracts.

In the embodiment of the invention using. a movable scroll element that forms a cylindrical driven surface in conjunction with a scroll driver, which has a cylindrical driving surface for the desired contact force, is an important characteristic that the diameter D, of the spiral driver different from the diameter:

knife D_ is the driven cylinder surface. In Fig. 6A, the s ι

essentially a cross-sectional line 6A-6A along in Figure 7, the diameter D_, the inner wall 38 serving as a driven cylinder surface is greater than the outer diameter D ^ ■ the ring 45 serves on Spiralenmitnehmer 35, the \ as a driving cylinder surface . The difference between D_ and Dj is>

s o. y

in Fig. 6A for a better representation of the forces j because of excessively large. Due to the difference 1, this diameter of the Spiralenmitnehmer shown in Fig. 6A ^ through the ring 45 results in essentially a line of contact to j abwälzende at L with the movable Spiralele- \

ment, which is represented by the inner wall 38. ;

The moving spiral element is in the radial-tangential | plane held by forces, 'which on the inner wall 38 as in i Fig. 6A attack (the constant representation; because of it is assumed that the center C of the movable! Spiral element or its drive ring the origin of the j involute of the spiral element as well as the center of gravity of I. movable spiral element reproduces). This on the movable j

Forces acting on the spiral element via the wall 38 are the.; Centrifugal force m ^ R _or and the tangential force F _t · the path radius R ^ of the spiral driver becomes smaller than the path j

409881/1012 - 25 -

radius R of the movable spiral element, a centripetal force results, which represents an inwardly directed radial force F. The size of F is a function of the contact angle, which in turn is a function of the difference between the orbital radii R _Qr and Jl and the difference between the diameters D and D. The contact angle θ between the scroll driver and the movable scroll member can be expressed by the diameters and the orbital radii as follows

sin θ = 2 (R _or - R _od ) / (D ₈ - D _d ). (1a)

For a given operating speed and fluid pressure θ is designed so that there is an appropriate, but not excessive, radial sealing force in the device

ο results, which is always smaller than the centrifugal force mCoR _QV on the spiral element describing a path, as stated above.

Ss is also within the scope of the invention to form a movable scroll element as shown schematically in Vig. 6b is shown, which has a driven cylindrical surface 38a, never a shaft instead of the inner wall 38 of the housing ring, wherein a spiral driver is used which has an inner driving wall 45a with a diameter larger than that of the driven surface 38a instead of the outer wall of the l: piston-like spiral driver forms. In this execution; form is therefore D, greater than D. However, R, remains greater than:

CL S ΟΓ

^: \> d ¹ ^ ¹ * ³ " ^{the different} forces, which result in the contact or radial sealing forces, are comparable with the reverse case _: v / ie a comparison of FIGS. 6A and 6B clearly shows 6B, the contact angle θ is defined as i

sin θ = 2 (R _or - R _od ) / (D _d - D ₃ ). (1b) j

The geometric design, which adjusts the radial sealing force, also means that the effects of manufacturing errors and the consumption of material due to wear and tear are reduced!

"4 09 ~ 8βϊ / ϊθΐ ~ 2 ~ ' -26- '

will. If all of the centrifugal force were to act on the radial seal lines, there would be excessive wear and tear on the scroll elements. For example, the center of the path could coincide exactly with the center of the spiral path during the manufacture of the spiral driver. In such a case, 9 would have a component that oscillates with the fundamental frequency λ>. If the actual values of the numerator and denominator of equation (1a) or (1b) are designed, for example, about ten times larger than the expected manufacturing error, the result is less than 10% double the peak value of the radial sealing force compared to its constant value.

7 and 8 show in detail a compressor which is directly connected to an electric motor as a drive device: is. The drive device shown is the one described in connection with FIGS. Figs. 7 and 8 clearly show the absence of any device restricting radial freedom of movement, apart from the abutment forces that act along the 3erUhrungslinien of the arch elements occur. They are different Embodiments of the coupling device shown, which is only connected to the spiral elements. The spiral elements and the spiral follower are similar to the components shown in FIG.

As FIG. 8 shows, the fixed spiral element 25 has two spiral-shaped arch elements 60 and 61 which form the surfaces with the lines of contact, these arch elements ending at their inner ends in widened sections 62 and 63 which are designed in this way that they with similarly widened ■ inner sections 64 and 65 of spiral-shaped arch elements 66 and! 67 of the movable spiral element form a substantially rectangular central fluid pocket 68 which represents the region of the highest fluid pressure. The flat inner surfaces (e.g., I the surface 69 of the enlarged inner portion 62 of the arch element 60) of the four inner portions of the spiral arch elements allow a small square coupling element 70 to be used, which serves to hold the movable scroll i

409881/1012 - 27 -

element 30 can move along its path without rotating with respect to the stationary scroll element. Since the coupling element is located within the fluid pocket with the highest pressure, it must be designed so that there are fluid passages within the pocket which communicate with the make both openings 21 and 55. It therefore has relatively large cutouts 80 on each side and similar cutouts on the top and bottom, leaving a centrally located compact piece. Rectangular sealing plates 84 are attached to each corner and are flattened or beveled to allow fluid communication between an outer fluid pocket and the inner fluid pocket through the two recesses 86 and 87 formed in the side plate 26 of the fixed scroll member . As. Figs. 8 shows, is of the fluid bag 90 via the recess 86 and the cutout 80 has a fluid connection with the ^in: tte of M ^ located bag exist. While the movable scroll member moves further along its path, _"shifts, this fluid connection using each of these recesses 86 and again 87th

The stationary spiral element 25 according to FIG. 8 can be designed in this way be that it has a lip 95 which forms the sealing surface 28. For the inlet of the fluid, e.g. B. air, into the device an opening 100 is provided in the side plate 26.

9 to 12 show embodiments of compressors according to the invention, in which the spiral elements are two complete; have spiral-shaped arch elements, which the surfaces \

with the lines of contact, as well as a circular coupling element. In FIG. 9, the same reference numerals as in FIG. 7 are used to designate corresponding components j. '|

According to FIG. 10, the stationary spiral element has two arches j

elements 140 and 141 and the movable scroll element two j

Arch elements 142 and 143 in the shape of an involute spiral \ on. The coupling device for connecting the stationary

with the movable spiral element has a ring 144, ■

4 09 881/1012 - 28 -

the diameter of which is sufficiently large that it can surround the surfaces of the spiral arch elements. As shown in detail in FIGS. 11 and 12, this coupling ring 144 has oppositely disposed flat sections on the inside which are somewhat thickened ^; T. ^r andab cuts 145 and 146 form on the ring. Cutouts 147 and 148 are formed on one side (for example the underside according to FIGS. 11 and 12), while cutouts that are opposite one another are formed on the opposite side of the ring 144

149 and 150 are provided, the axis of which is perpendicular to the axis of the cutouts 147 and 148. . ¥ ie from Figure 10 is clear, 140, the sheet member of the stationary scroll member a radial shoulder 155 on which it sawn ■ solidifies or is with this in one piece and so: is arranged and designed such that it into the cut 147 of the ring engages. In the same way, a radial extension 156 fastened to the arch element 141 engages in the cutout 148

one, while one on the arch element 142 of the movable scroll:

element attached radial extension 157 slidable in the ^! Cutout 149 and one attached to the arch element 143

radial extension 158 also slidable in the cutout;

150 lies. While moving on the track, they are; radial attachments in the cutouts can be moved freely, while ■ the spiral elements cannot perform any relative angular movements. One or more low-pressure openings 159 are arranged between the ring 144 and the outermost arch elements j,! while a central high pressure port 16O communicates with i of the high pressure zone. \

The modified construction according to FIGS. 13 and 14 is designed as follows

mitj '

states that many relatively small outside diameters receive high compression ratios. The control of the openings in this off-i guide shape is designed so that the high pressure port opens intermittently and the spiral driver intermittently is acted upon by the gas pressure when the high pressure port is released. This arrangement allows the axial loading possibly a function of the angular position of the spiral driver and a function of the pressure supplied

409881/1012 - 29 -

As shown in Figo 13 emerges _9, the sheet member 270 on the stationary scroll member a involute wrap with a Umlaufj having a semicircular face approach 271, the edge of which is an involute curve (shown in Figure "13 by dashed lines) at its base and the two radial lugs 272 and 273; which engage in corresponding cutouts in the coupling ring 274 «,

The side plate 275 of the stationary scroll element together ^: with a ring element 276 and a flange 277 form part of a housing _? the one chamber .278 results in ₉ in which the movable scroll element and the spiral driver are arranged o An eccentric high pressure port 279 establishes a connection between the high pressure area of the device and a line (not shown) _o A circumferentially arranged low pressure port 280 provides a fluid connection with the ■ surrounding atmosphere or a not shown low pressure

The movable © spiral element has © in Bog @ neleaent 281 ₉ ; that at the inner end © in © inem widened Absdsnltt 282 from- =

runsj, whose cross-sectional shape is determined by a circle and © ine _: involute _{curve o} The arch element 281 points

a face 283 having an involute outline on it;

Base and two radial lugs 284 and 285 for engagement>

with the coupling ring 274 on * the enlarged middle section ^)!

282 of the arch element on the movable scroll element is provided with '< a narrow fluid passage 286 ₉ which is defined by the height dimension j

this section extends, and with a high pressure port 287!

provided, which shows _P as in Fig. 14 ρ a short distance \

up into the widened section 282 of its attachment; This fluid passage 287 has a jagged surface

cut out edge and an arcuate edge, the j

Purpose from the description of the operation of the device ' is evident o

409381/1012

The spiral carrier 35 and its associated bearing 47, the The pretensioned spring 53, the ring seal 52 and the sealed space 54 are similar to those described with reference to FIGS Elements.

The main housing is completed by a housing part 288 which is fastened to the flange 277 by suitable means such as screws, bolts 289 and which has an extension 290 in the middle for receiving the shaft. The shaft 291 of the spiral carrier pail with the axis 291a ends in an eccentric shaft section 292 with the axis 292a, the distance between these parallel axes R- _{O (} p being the radius of the spiral carrier. The shaft 291 is in the shaft housing 290 by means of bearings 293 and the bearings are spacer ring 295 and a shaft seal 296 at a distance ^r% oneinander held 293 and 294 are held by a ring 298 in position: .294 rotatably mounted, by a..

In contrast to the arrangement according to FIG. 7, the movable spiral element is not frictionally for sealing against the housing section of the stationary spiral element at ₉ while it describes its path. Rather, the seals between the end surfaces of the sheet members VNA the surface approaches 271 and formed 281, such as the Figo 14 showed the low pressure = fluid passes through the aperture 280 in di © chamber 278 and through passages between the curved elements and the flat lugs ₉ as for example the passage 299 into which the hied © räracktaschen _s formed by the spiral arch elements ιί @ τ & θώ, _β

In the following description of the operation of the embodiment according to FIGS. 13 and 14, it is assumed that the device operates as a compressor ■ off pocket "has seals so that the enlarged portion 282 of the arc j ^r covering elements on the movable scroll member, the high pressure port 279 '. While the arch element 281 moves on its path. ' away, the.jopening _279 is "covered." and.released, _.so that j

40988 1/10 12 - 31 -

immediately before the opening 279 is released, the volume 300
is decreased so that the fluid pressure is increased. The volume
300 is further decreased while fluid passage 286
opening 279 begins to uncover, whereupon it completely
is released until the volume 300 reaches the value zero, at which time the opening 279 is closed again
will. After opening 279 is completely closed,
the arch element 281 moving on its path closes
from the chamber, which is open to the low-pressure side, so that
a high pressure chamber 300 is formed and a new cycle
begins.

The intermittent charging of the sealed space 54 with
High pressure fluid through passage 286 occurs during
Period of the cycle during which passage 286 is in communication
with the high pressure port 279 is. During the remainder of the cycle, the high pressure fluid is held in the sealed space 54 until there is a new charge of pressurized gas
receives. This intermittent opening release in the dispensed _; sealed space has the advantage that it is possible to change the axial sealing forces directly with the axial gas forces,
exerted by the movable scroll element, and hence the difference between these two opposing ones
To keep forces approximately constant. In addition, the phase is; of the drive shaft with respect to the open state of the opening 286, whereby a balance between the axial gas force and the loading force can be achieved, as explained above: was. j

The device according to FIGS. 13 and 14 is, although it is different various advantages as a gas compressor or expansion machine, not suitable as a liquid pump because the inter- i

central opening control is available. j

As stated in the general description of the invention ¹ , the desired relative movement of the cylindrical surfaces,
which the variable fluid chambers of the displacement device,

409881/1012

form, can be achieved in that a spiral element is stationary is arranged and the other describes a path without any relative waving movement taking place, or thereby, that both spiral elements execute a vortex movement about their respective parallel axes without any relative angular movement the spiral elements occurs. The devices shown in the previous figures operate according to the first one Operating mode.

In the apparatus of FIGS. 15 and 16, the second mode of operation is used. So much for the spiral arch elements and couplings can have one of the shapes indicated above: these components are not further described. So are both; for example the arch elements on the spiral elements and the; Coupling according to FIG. 9 for the corresponding components in FIG. used and the same components are provided with the same reference numerals as in FIG.

The stationary scroll element of the previous embodiments becomes a driving scroll element generally associated with and the movable scroll member becomes a driven scroll member indicated at 305. That The driving scroll member 304 has a side plate 306 and an annular outer wall 307 that is in an annular sealing surface 308 ends, which is identical in function to the sealing surface 28 in FIG. 7. The side plate 306 of the driving Spiral element 304 is attached to a shaft 309 or formed in one piece with this, which has a in the middle Has low pressure channel 310, which extends over its length up to extends the point where the shaft is connected to the side plate. This channel 310 is the low pressure inlet encoder Outlet) line and it is therefore necessary to provide a device for this channel 310 so that it can with the outer low pressure chambers can be connected. this will reached by a transverse channel 311, which is in the Approach 312 is arranged on the underside of the side plate 306. This transverse channel 311 ends in an or

multiple openings, e.g. B. the openings 313 and 314 shown in

409881/1012 - 33 -

the side Platt drilled © 506, as shown in FIG _o 16 plays the violin.

The drive shaft 309 is in a housing from section 315
rotatably mounted and it is aligned by bearings 316 and 317
held by a spacer 318 at a distance
_o An externally threaded section 319 of the shaft allows it to be screwed on
a threaded ring 320 for holding the bearings »On the housing section 315 is a housing 321 for a pulley and
the shaft is fixed and the drive shaft 309 terminates in a
Extension 322 of this housing _o For the seat of the shaft is
an elastomeric ring 323 and a ring retainer element 324. The housing extension 322 has a threaded portion
provided passage 325 on _{9 of} the with the channel 310 in the shaft
is aligned _o This threaded passage is used
for the connection of a suitable line ^ if one
A belt pulley 326 and the driving spiral element 304 are attached to the shaft 309 for its drive. It is driven by a motor 327 via another ©
Belt pulley 328 and a cellular belt 329ο Any other suitable device can also be provided ₉ by: which sets the W © 11 © 509 in a rotary motion \ τΙτά ₅ wi ©

© in gear ο

The driven scroll element 305 is generally identical in structure
with the above-described movable scroll element and © s; has a side plate 335 with a sealing surface 336 on the circumference ₉ and a _{ring extension} 337 which surrounds a space in which the spiral driver is arranged, which is generally designated 338. The elastomeric ring 52 and the pretensioned spring 53 are identical in function to the components described above and the spiral driver 338 differs; of the one described above in that it is attached to a shaft 339; is attached or consists of one piece with this ^ the · | © has a channel 340 for the high-pressure fluid, which is continuous! is formed, "Di © shaft 339 is rotatably supported in the housing section 341 'by bearings 342 and 343 _p by a

4098 81/1011 -34

Spacers 344 are held at a distance from one another. On an externally threaded portion 345 a ring 346 is screwed onto the shaft 339 and serves as a holder for the bearings. At the end of the housing section 341 is a housing 347 is attached, the shaft 339 terminating within an extension 348 of this housing. To seal the Shaft 339, an elastomeric ring 349 and a ring holder element 350 are provided. The housing extension 348 has one that is threaded provided passage 351 which is aligned with the channel 340 of the shaft. At this threaded passage can a line can be connected.

The high pressure channel 340 opens into the sealed space 355, which has the same function as the space 54 in FIG. The high pressure port 356 provides communication between the high pressure chamber 357 and the space 355 and the high pressure channel 43.

In another arrangement, the low-pressure inlet into the spiral elements can be space 359 formed by housing sections 315 and 341. In such a modification, the low-pressure opening into space 359 can be formed by a passage between the housing sections ij @ rü, en _o DI® housing sections must be connected by a seal or the space 359 must be closed in some other fluid-tight manner ₀ In this embodiment, the channels 310 and 31I ₉ di © openings _: 313 and 314 _S, the shaft seal 323 and the annular outer wall 307 on the spiral element 304 “Die bearings must then, however, work "in the operating medium, unless they are suitable shaft seals before fiiesem protected _o in many cases, those shaft seals not required [

During operation of the device according to FIG. 15, the driving spiral element 304 is set in rotation about its axis 560 , whereby it displaces the driven spiral element 305 from its axis 361; rotates ₉ which lies parallel to the axis 360 and has a distance from it that is equal to the radius R. of the spiral driver [is. The contact between the arch elements de? both spiral,

elements occurs along a number of lines of contact, ζ. Β. ί . ... . ι

409881/1012 - 35 -

the contact lines A to D in Fig. 1, the mode of operation of the device is the same as that in connection with the. Figs. 1 to 4 described. The driven scroll member 335 is floating with respect to spiral follower 338 to provide axial sealing in the same manner as above. described receives. Likewise, the diameter D ^ of the spiral ' driver smaller than the diameter D of the inner wall of the Ring shoulder 337 on the driven spiral element 335 so that you can ■ receives the required radial sealing force.

Since each spiral element carries out its gyratory movements in a self-balancing manner, no counterweights are required. _: This is an advantage of the embodiment according to FIG. 15. Another advantage is that no inertial forces are transmitted via the bearings, so that very high speeds and a correspondingly high capacity can be achieved.

If necessary, the role of the two spiral elements can be reversed. For example, the spiral driver can over a suitable device can be connected to the engine, so ■ that the scroll element 305 becomes the driving scroll element and the scroll element 304 becomes the driven scroll element. ;

In another embodiment of the device , the disadvantages of the known devices are thereby eliminated; or reduced to a minimum that the entire centrifugal ^; force or part of the centrifugal force acting on the spiral element describing a path is balanced and the spiral element moving on a path is compensated by a mechanical connecting device which is flexible in the radial direction!

the drive device is connected. If all centrifugal ■ forces are balanced, the resilient mechanical 'connecting device is designed so that a radial force j component of the desired size is present, which is the radia-j-Ie Sealing causes. If less than the entire centrifugal! force is balanced, the part that is not balanced is used for radial sealing. The axial

409881/1012 "-36-

Sealing is achieved by two opposing forces acting on the spiral elements. The first force is generated by a pretensioning device including the fluid pressure, which acts on the fixed spiral element, and the second force is applied to the spiral element describing a path via the coupling device, which is arranged outside the spiral pockets, whereby it is the force of the pretensioning device is opposite. The coupling means, which maintains the desired angular relationship of the scroll members, operates independent of the radial sealing forces, which are independently controlled, so that the wear on the ^loading: rührungslinien is recycled between the sheet elements of the scroll members to a minimum and non-compressible impurities can be compensated, which can accidentally get into the fluid pockets.

A compressor designed in this way is shown in FIG. 17 in a longitudinal section. Reference is made to Figures 18-28, 30 and 36. In all of these figures, the same reference symbols are used for the same components. As FIG. 17 shows, the fixed scroll member which is generally indicated at 71, a side plate 72, a sheet member 73 with more than three rounds (Fig. 22) which terminates in a broadened peripheral portion 74, a · seal ring 75 and an extension 76 arranged in the middle.: A high-pressure channel 77 is formed within this extension 76; forms, in which a connecting pipe 78 extends, which is aligned with the machine axis 79 and for the connection; a high-pressure line, not shown, is used.

The spiral element 81 moving on a path has a side plate 82 and an arch element 83 with more than three revolutions, which ends in a widened peripheral section 85 (FIG. 22). To achieve the axial seal, the ι end face 89 of the arch elements 73 and 74 must be on the stationary; Spiral element closely abut the inner surface 91 of the side plate 82 ^{] of} the movable spiral element, and in the same way the end face 92 of the arch elements 83 and 85 must

409881/1012 - 77 -

movable scroll member tightly against the inner surface 93 of the fixed scroll member. To achieve the radial sealing, the arch elements of the two spiral elements must form lines of contact by rolling, z. B. the Lines of contact 94, 96 and 97 in Figure 22. The innermost fluid pocket 98 forms the area of highest pressure, while the filled one Chamber 99 around the arch elements represents the area of lowest pressure. The fluid pockets 111, 112 and 113 (Fig. 22) have intermediate pressures that increase toward the center pocket 98. This area of highest pressure is in communication with a high pressure line via an outlet opening 77 and a connecting pipe 78. The low pressure chamber 99 is in communication with a low pressure fluid source or reservoir via one or more low pressure ports 114. if the device works as a compressor, becomes low pressure fluid introduced through the opening 114 and drawn off the compressed fluid via a line connected to the connecting pipe 78. On the other hand, when the device is used as an expansion machine, the high pressure fluid is passed through passage 77 introduced and the expanded low pressure fluid through a or multiple openings 114 withdrawn.

22 explains a possible embodiment of the spiral-shaped Arch elements that can be used in the device. Arch elements with more or less can also be used can be used as three circuits, whereby these arch elements can also be designed differently than in the form of a real one Spiral (z. B. as a deformed circle) and at its inner ends to control the volume of the high pressure pocket certain shape ■ may have conditions. A number of such suitable shapes of the arch elements are disclosed in U.S. patent application Serial No. 368 907 specified.

The device with the spiral elements is in a housing 125 arranged, which in the embodiment of FIG. 17 is a front Has cover plate 126, which is fastened by means of screws 127 to a housing rear side 128, which in turn

409881/1012 - 38 -

a rear cover 129 is covered. The low pressure port 114 is formed in the front cover plate 126.

The fixed scroll member 71 is secured in the front housing cover plate 126 and aligned by a sealing ring 75 and a central boss 76 that is secured to, or preferably is integral with, the outer surface 200 of the side plate 72. The front cover plate 126 has an internally disposed retaining ring 201 and a centrally disposed bore 202 (FIG. 18), each of which is provided with a circumferential groove for receiving an elastomeric sealing ring 203 and 204, respectively, and these sealing rings provide a seal with the Ring 75 and the approach 76 ago. As FIG. 18 clearly shows, the ring element 75 ends shortly before the inner surface 205 of the front cover plate 126, so that a flat annular space 206 is created in which a wave-shaped spring ring 207 is arranged, which exerts an axial force on the stationary spiral element 71 exercises. This force forms part of the required axial sealing force. An additional axial sealing force is obtained in that pressurized cooking fluid is introduced into the annular space 206 and into the sealed annular chamber 208 (between the ring 75 and the extension 76) via the opening 209, which in turn is connected to a high-pressure fluid source (not shown). This high-pressure fluid source can be external, for example a storage tank with nitrogen, or the area of highest pressure in the device, e.g. B. the high pressure bag 98 can be used. In the latter case, connections (not shown) between the pocket 98 and the chamber 208 must be established. When the high pressure fluid is being supplied from the highest pressure area within the device (i.e. from the pocket 98), the axial force exerted by the: undulating spring washer 207 must be sufficient to provide a seal during start-up, since at this stage of operation, if at all, only ^: little high-pressure fluid from the pocket 98 is available. ; If, however, as in the case of the embodiment according to FIGS. 17 ■ and 18, the high-pressure fluid for the axial sealing of an i

409881/1012 - 39 -

is supplied from an external source, it can be introduced into the chamber 208 prior to start-up, with the supply up to to turn off the device.

The fixed scroll member is arranged at a certain angle relative to the front housing cover plate 126 and it is fixed in this position relative to the housing by fastening elements 210. These fasteners after Figures 17 allow a slight adjustment of the angular position of the fixed scroll element during assembly or operation so that it is at the optimal angle. The fastening elements consist of a screw bolt 211 with thread 212 and a screw head 213, on the eccentric a pin 214 is attached to the bolt axis. At 215 there is one Called mother. The pin 214 engages a recess formed in the rear of the side plate 22 (Fig * 19). Because of the eccentricity of the pin 214 relative to the bolt axis, a rotation of the screw bolt 211 results in that the pin 214 and thus the side plate 72 of the fixed spiral element is displaced over a small angle, so that you can set the optimal position for the fixed spiral element. On the other hand, the fastening element also be a simple constant diameter bolt extending from within the front cover 126 in extends the incision 216, in which case the angular position of the fixed spiral element is not adjustable.

In the embodiment of FIG. 17, the spiral elements cooled by a coolant circulating in the side plate 72 of the fixed scroll member, as shown in FIG. 19, which shows a view of the outer surface 217 of this side plate 72. In the side plate 72, a plurality of them are communicated with each other standing channels 218 are drilled, which form a network of pipes, which via suitable connections 219 and 220 to not shown Lines is connected through which a coolant can be introduced and withdrawn again.

A 0988 1/1012

In the embodiment shown, it is used for lubrication of the end faces 89 of the arch elements of the fixed scroll element uses a lubricant. As from the partial views 20 and 21 shows the coming to abut, spiral-shaped end face 89 of the continuous Arch elements 73 and 74 have an oil groove 221. The lubricant is applied to the outermost portion of the groove via a line 222 fed, which is connected to an opening 223 which is drilled in the widened arch element 74 and extends to extends to the groove 221. The lubricant is pressed through the groove 221, which extends over the entire arch element, any excess lubricant flowing by gravity to the bottom of the housing, where it flows through a Opening 224 can be withdrawn (Fig. 17). The lubrication of the end faces of the arch elements coming into contact is especially not required in cases where the corresponding surfaces on the arch elements and the side plate consist of a self-lubricating material or are not subject to excessive wear, or even if the duration and type of operation either do not require it or the introduction of a lubricant in the device even forbids.

The spiral element moving on a path must be prevented from moving out of the angular position with respect to the fixed spiral element and the housing, and it must be driven on its path in such a way that all or part of the centrifugal force that occurs during the movement is' of the web occurs, is counteracted, whereby for require \ derliehen radial sealing forces will be provided. -

The maintenance of the angular position between the movable scroll element and the fixed and the housing is achieved by a coupling element 225 reaches. As Figs. 24 to 26 show * this coupling element consists of a ring 226 with an H-shaped cross section. The front 227 is the movable one Spiral element opposite, while the rear side 228 of the inner wall 229 of the housing part 230 faces (FIG. 17). The front

409881/1012 - /,> ■ -

side 227 has two opposing keyways 231
and 232 (Fig. 24). The back 228 is also with
two opposing keyways 233 and 234 are provided. The axes of the keyways on the front and back
are at right angles to each other. The slidable: wedges engaging in these keyways are on the
a orbit moving spiral element and on the housing part 230
attached. As FIGS. 17 and 23 show, the wedges are 235
and 101, for example by means of countersunk screws 102 in flat
Recesses 103 and 104 attached on the outside

105 of the side plate of the movable scroll member are formed. These keys slide in keyways 231 and 234

of the coupling element. Fig. 27, which is a view of the inside = 229 of the housing part 230 shows the arrangement of the wedges

106 and 107 again, which are secured by countersunk screws 108 (Fig. 28) in
Recesses 109 and 110 are attached to the surface 229.
These keys 106 and 107 slide in keyways 233 and 234. \

As far as sliding friction between the front and rear sides _; of the coupling element and the surfaces of the side face
the movable scroll element and the housing part is present, it may be useful to lubricate these surfaces.

In the embodiment according to FIG. 17, this is done by introducing of oil through opposing bores 115 and 116

(Fig. 27) reached in the housing part 230, which with arcuate '

Grooves 117 and 118 on the surface 229 of the housing part in ' Connected. The one flowing through these arcuate grooves!

Oil enters a lubrication groove 119 on the back 228 of the [

Coupling element, whereupon it has short arcuate grooves j

121 and 122 through holes 123 and 124 (Fig. 24 and 26) through |

the coupling element in a lubrication groove 120 on its front |

page 227 reached. If necessary, excess oil will flow!

from the coupling element down through the vent opening 224.!

• For some devices it may not be appropriate to use a J To use lubricants or to tolerate the losses caused by friction between the coupling element and the j

surfaces adjacent to it, as it is.

409881/1012 -42-

management form according to Fig. 17 is the case. It is possible on _; to dispense with a lubricant and at the same time substantially reduce the friction losses by using a coupling element with rolling elements, as shown in FIGS. 29 and 30. The coupling element 236 is a ring with essentially the same cross-section as the coupling element. 225 of FIGS. 24 and 25 and it has keyways 231 Ms 234, as indicated above. However, it is supported by three sets of rollers 237, 238 and 239, each set having a plurality of rolling elements or rollers 240 which abut the face 241 of the coupling element and the surface 105 of the movable scroll element, and a plurality of rollers 242 which rest on the The rear side 243 of the coupling element and rest on the surface 229 of the housing part 230. The cylindrical rollers 240 . and 241 are aligned at right angles to each other and their axes are perpendicular to the axis of the keyway on the surface they bear. This means that each roller can move with the coupling element while it is moving in the directions of the arrows (FIG. 29).

During the embodiments of the coupling elements shown in FIGS. 24 to 30, splines in the coupling element and slidable show engaging wedges on the movable scroll element and on the housing part, it is also possible to reverse this arrangement and attaching the keys to the coupling member to provide the keyways in the movable scroll member and the housing portion.

17 and 31 to 35 different embodiments are shown: a suitable mechanism for driving the spiral element moving on a path with the required radial direction; Resilience shown, through which the predetermined radial sealing force is achieved. This device, which is flexible in the radial direction, can take various forms. It is also possible | lent to choose between different modes of operation, ie ί offset part of the centrifugal force and using the \ portion which is not balanced, so radial sealing force, j or balance substantially all centrifugal force and arrangement of a device in the mechanical yielding: ■ - - - 43 ^Y -

40 9881/1 012

Connection to achieve a radially outwardly directed force that can only serve as a radial sealing force.

In the embodiment of FIGS. 17.31 and 32 is the

Mechanical connecting elements which are flexible in the radial direction

direction a rocker, while according to FIGS. 33 to 35 i

is designed as a slider. In these two execution;

compression springs can be used throughout the j Centrifugal force or a part of it counteract it, or it can instead of springs or in addition to the springs Counterweights are used.

In order to obtain radial compliance, the spiral element moving on a path must move inwards or outside relative to the device axis depending on the gradual wear of the arch elements on the spiral elements or to compensate for non-compressible objects, such as fluid accumulations, wear residues or accidentally penetrated dirt particles. This radial compliance also allows the use of less precisely designed spiral elements in that the j Spiral element can move within the fixed spiral element and its path if necessary: to adjust the geometric configuration of the arch elements' of the two spiral elements can be set. With the execution j 17, 31 and 32 is a ball bearing on an axial drive shaft of the spiral-j moving on a path element arranged, the outer circumference of this ball bearing j being connected to a crank mechanism with a rocker: The axis of the rocker in Fig. 31 is normally perpendicular to the radius of eccentricity of the one moving on a path Spiral element. During the rotation of the driving crank, the moving spiral element swings under the Effect of the centrifugal force acting on its center of gravity radially outwards. The spiral element moving on the path | is due to the contact with the arch element of the fixed ' Spiral element to a given geometric path

09881/1012

bound. The radial contact force between the moving ■ and the fixed scroll member is adjusted by mechanical springs or equivalent devices to provide an i predetermined part of the centrifugal force acting on the moving scroll element: is balanced. ;

In FIGS. 17 and 31, the spiral element moving on a path is driven by the main drive shaft 244 which is arranged in a bearing 245 in the rear cover plate. A crank 246, to which a connecting rod 248 is articulated via a bolt 249, is fastened to this drive shaft 244. This connecting rod is attached to the moving spiral element via a stub shaft 250 by means of a snap ring 256 and a ball bearing 251 with an inner race. ring 252 and an outer race 253, the latter being attached to the ring 254 of the connecting rod. The axis of the shaft 250 is denoted by 255 in FIG. 31. The axis of the main shaft and the device is the same as that of the fixed scroll element and is therefore designated 79. The distance between the axis 255 of the moving scroll element and the device axis 79 is the orbit radius R _OI> .

Since the device is expediently described as a compressor, the main shaft 244 is connected to a motor in the illustration 257 connected. As indicated above, however, it is also possible to use the device as an expansion machine, wherein in this case the device 257 as a suitable consumer, e.g. B. as a compressor or as a brake in the case of a refrigerating expansion machine.

The swing arm, which consists of the connecting rod, the ball bearing and the bolt, is connected to the crank via an or several compression springs are connected, as shown in FIG. 31. A T-bolt 153 is attached to the connecting rod 248, the extends through the wall of the crank 247, the flat countersinks 154 on its outside for receiving concentric

Has springs 161 and 162, which by a spring plate 163

409881/1012 -45-

be held in a compressed state attached to the ·. T-bolt 153 fastened adjustably by means of a nut 164
is. By turning this nut 164, the springs 161 and 162 are pretensioned to a certain force. The number of i springs and the degree of preload can be chosen so; that a predetermined portion of the moving scroll; element attacking centrifugal force is balanced, while it completely traverses the eccentric path. The springs pull ■ thus on the rocker in the opposite direction and ■ thus exercise a centric on the moving spiral element. petal force from, being the difference between the centrifugal; and centripetal forces substantially equal to the radial
Sealing force is. This in turn means that the radial sealing force can be adjusted by adjusting the degree of pretensioning of the springs. ^j

During start-up and shutdown (as well as in operating states in which the spiral element does not move along its path) the springs push the rocker inward, i.e. towards the inner surface 165 of the crank, so that the - \ The small gap 166 shown in Fig. 31 does not exist. ; This means that the radius of eccentricity of the move-; the spiral element is slightly smaller than the normal orbit radius; during operation. As the speed of the device increases, the centrifugal force on the moving spiral element increases and reaches a point where it corresponds to the holding force of the springs and eventually reaches it
a value greater than the spring force. That way is
initially when starting up and during the last section of the
When the device is switched off, there is no contact with the arch elements
present on the spiral elements. This in turn means
that the motor 257 driving the shaft 244 is not under load
must start, but only takes on the load while the
Speed increases. The same advantageous condition results
also during shutdown ₀

In the embodiment described, the axis of the rocker lies

409881/1012 - 46 -

perpendicular to the radius of eccentricity of the describing a path: Spiral element. This has the advantage that the radial sealing force does not change when the inlet and outlet

change the conditions of the device. :

Modifications to the structure of the rocker arrangements shown in FIG. 31 are possible. An example of such an ab-; Conversion is the use, 'the centrifugal force exerted by the moving scroll member is equal and opposite to a counter weight on the rocker, which exerts a force on this. Such a counterweight can be attached to the spring plate 163, or the spring plate itself can be designed so that it acts as a counterweight. When a> counterweight is used to balance the total centrifugal force, the springs, e.g. B. the springs 161 and 162 'or a single spring to generate the radial sealing force. Such a configuration in turn enables an accurate; Control of the radial sealing force. In addition, the ί combination of springs and the counterweight, the radial sealing force independent of pressure changes at the inlet and outlet enables' the machine, j as well as to make independent of changes in operating speed. |

Two further modifications of the rocker are shown in FIG given. In one case, the springs are replaced by a counterweight i 167 which is attached to a ring 254 of the connecting rod 248 j is attached or consists of one piece with it and extends out of an opening 168 in the crank 247. Here! the counterweight 167 is designed so that part of the centrifugal force acting on the moving scroll element is compensated, while the remaining portion is used as a radial sealing force of a predetermined size. The counterweight 167 thus serves the same purpose as springs 161 and 162.

The second modification shown in FIG. 32, which is applied in the same way to the rocker shown in FIG. 31 can be, is that the axis of the rocker is so arranged ..._ that it_ with the eccentricity radius of the

409881/1012 -47-

a path moving spiral element forms an angle of less than 90 °. This results from a shift in the Articulation axis 249 of the rocker relative to axes 79 and 255. The reduction of this angle has the advantage that the size of the counterweight or the spring can be reduced to compensate for the acting on the movable spiral element Centrifugal force is required. However, this means that the resulting radial sealing force is somewhat dependent on the pressure changes depends on the inlet and outlet of the machine.

It is also possible to use the mechanical, resilient connection

Means between the drive shaft and the spiral element describing a path by a mechanism with a slide in place of the rocker arm shown in FIGS. 17, 31 and 32 form, as shown for example in FIGS. 33 to 35, in which the same reference numerals for the same Elements as in Figs. 17, 31 and 32 are used. On the cross-sectional, front and side views of FIG. 33 through 35 it can be seen that the crank 180 has a flat contact surface 181 on which a surface 182 of a slider can slide 183 is applied, which is displaceable in a courage formed in the crank 180 (Fig. 35). This slider 183 is on a flanged stub shaft 184 or the spiral element 81 describing a path via a bearing arrangement attached, which comprises an inner race 192, an outer race 193 and balls 194, this ball bearing is inserted in a holder 195 which is arranged on the rear side 196 of the slider 183. The crank 180 is connected to the slider 183 preferably via a compression spring 186 (FIG. 33), which is attached to the inner wall 187 of a Chamber 188 is fixed in the slide and on a holder 189 which is formed as a projection on the crank 180 and extends into chamber 188. This spring 186 plays the same role as the springs 161 and 162 of the embodiment according to Fig. 31, i. H. it compensates for part of the centrifugal force acting on the spiral element describing a path. As with the swing arm arrangement, it is also possible here to replace the spring or in addition to the spring in the same .....

409881/1012 - 48 - _

Way to use a counterweight as indicated above. Such a counterweight 190 is shown in FIG. 34, wherein it is attached to the slider 183. The connection of the slide according to FIGS. 33 to 35 is preferably with the coupling element according to FIGS. 17 and 24 is used j d. H. ! that the coupling element under sliding friction on the housing; part and rests against the spiral element describing a path. The advantage of this connection by means of a slider is; that it can absorb the axial holding force applied to the one Attacked the path described spiral element, so that the coupling element is relieved in the axial direction and therefore ' less power consumed. I.

As shown in FIGS. 17 and 36, the drive mechanism also has opposing counterweights, which consist of a; first counterweight 170, which is fastened by means of screws 171 to a shoulder 172 of the crank 246, and a second j Counterweight 173 exist, which is fastened by means of screws 174 to a flange 175 of the crank 246. The opposite, Weights are designed in terms of size and arranged on the crank in such a way that vibrations when the machine is running turned off. The larger counterweight 170 is arranged so that a centrifugal force in the same direction as the centripetal force of springs 161 and 162 (Fig. 31) is exerted.

The method of operation of the device according to the invention is explained in detail above with reference to the various components been. The overall operation of the device can therefore be briefly summarized, particularly taking into account working as a compressor or as an expansion machine. In the case of a compressor, the low pressure fluid, e.g. B. Air from the surrounding atmosphere, sucked in through one or more openings 114 and as compressed air via the high pressure line 77 delivered (Fig. 17). As the spiral element 81 moves along its path, it becomes through the coupling element 225, which is arranged between this and the housing part 230, against the fixed spiral element_71]

4 09881/1012 "~ -49-

the force of the wave-shaped spring ring 207 and the fluid pressure pressed in the sealed fluid chamber 208 so that there is an axial seal between the end faces of the arch elements and the side plates of the spiral elements which abut against each other. The radial sealing by pressing the arc elements to form advancing lines of contact is to the extent desired by the proportion of Controlled centrifugal force, which is balanced by a centripetal force, which is flexible in the radial direction mechanical connecting device results.

When the device works as an expansion machine to deliver mechanical energy and / or cold, the gas to be expanded is introduced through the high pressure port 77 and. withdrawn via one or more low-pressure openings into a low-pressure reservoir. The formation of the axial and radial sealing is effected in the same manner as in the ^work: as the device as a compressor.

- 50 -. j

409881/1012

Claims (43)

Claims Ί, Ι device for conveying or treating a fluid, with an inlet and an outlet for a fluid and two spiral elements with arch elements which lead to Formation and sealing of at least one moving bag of variable volume and areas different fluid pressure forming advancing lines of contact, wherein a spiral element is drivable so that it moves relative to the other on a path while maintaining a fixed angular relationship to this is maintained, characterized by a drive device (35, 56) with a device (45, 38) for the formation of a centripetal radial force which counteracts part of the centrifugal force is, which acts on the spiral element (30) describing a path, the radial sealing force between the Spiral elements is kept at a value that keeps wear and internal leakage to a minimum. 2. Apparatus according to claim 1, characterized in that one of this drive device (35, 56) is separate and various coupling means (144) are provided and that the radial restrictions the freedom of movement within the device on these moving lines of contact (A, B, C, D) between the arch elements (10, 12) are limited and by this means for generating the centripetal Radial force can be controlled. 3. Device according to claim 2, characterized in that that the means for axial sealing comprises means (55) for withdrawing part of the fluid from the area of highest pressure (33) and a sealed space (54) for receiving the from the area of highest pressure withdrawn fluid, the axial sealing forces generated that are essentially proportional this, the highest pressure are. 4. Device according to claims 1 to 3, characterized in that that to supplement the axial sealing force of the fluid in the sealed space (54) a prestressed Spring (53) is provided. 5. Device according to claims 1 to 4, characterized in that the one spiral element (30) associated device for generating a path movement of this spiral element has a cylindrical driving surface (38) with a: orbital radius R _or and the Spiralelementantrlebseinrichtung (35) with a cylindrical drive surface (45) through which this spiral element (30) ^{executes a path movement via:} a line of contact with this cylindrical drive surface (38), the cylindrical drive _{surface (45) having a path radius R Qd} which is smaller than R _or , whereby during the path movement of the spiral element drive device (35) to achieve a driving force acting on this spiral element (30) this centripetal force is produced, which counteracts part of the centrifugal force acting on the spiral element, the difference between the centripetal and centrifugal force being the only contact force between the spiral elements (25, 30) bi ldet and the device for generating a path movement is connected to the spiral element drive device. 6. Apparatus according to claim 5, characterized in that the device forming the cylindrical driving surface (38) a housing (38) with an inner diameter D_ and the cylindrical drive surface (45) is designed as a piston whose outer diameter D- is smaller than D. 409881/1012 7. Apparatus according to claim 5, characterized in that the device forming the cylindrical drive surface has a shaft with an outer diameter D and the cylindrical drive surface is designed as a cylindrical housing whose inner diameter D _{d is} greater than D ₃ . 3. Device according to the preceding claims, characterized in that that the other spiral element (25) is arranged stationary. 9. Device according to the preceding claims, characterized in that that the spiral elements (25, 30) are rotatable on separate parallel axes, the distance between these axes are at least as large as the orbit of the one spiral element (30). 10. Device according to the preceding claims, characterized in that that the arch elements (10, 12; 60, 61, 66, 67) are designed as involute spirals or as circular arcs. 11. Device according to the preceding claims, characterized in that that the arch elements on each spiral element (25, 30) are two spaced-apart involute spirals, of one of which ends just before the center of the spiral element and the other highest to adjust the volume of the zone Pressure runs out at its inner end in a widened section (Fig. I3). 12. Device according to Claims 1 to 10, characterized in that that each arch element terminates in a widened section at the inner end. 13. Apparatus according to claim 12, characterized in that the widened sections of the arch elements in the middle form a rectangular space and the coupling device is arranged within this rectangular space (Fig.8). 409881/1012 53- 14. The apparatus according to claim 11, characterized in that the arch element of a spiral element on the inside! ends in a widened section and the j The arch element of the other spiral element is an involute j tspirale, the widened section being a Has passage, the one of the zone of highest pressure associated opening and a passage intermittently releases to which a line can be connected (Fig. 13). 15. Device according to the preceding claims, characterized in that the coupling device has a Has arch elements surrounding ring (274) with four equally spaced incisions, in which radial lugs are displaceable, which are formed on the arch elements. 16. Device according to the preceding claims, characterized in that the value of (D _g - D _d ) / D _{3 is} between approximately 0 _r 001 and 0.2. 17. Device according to the preceding claims, characterized in that the device which the spiral element j ment drive device issued a path movement, having a main drive shaft rotatable by a motor,! which rotates around a first axis, as well as an eccentric shaft which can be rotated around a second axis, which lies parallel to the first axis and has a distance from it that is not greater than the radius of the orbit of the one spiral element (30), this eccentric shaft being drivable by the motor. 18. The device according to one or more of the preceding claims, characterized in that the side plate of the stationary spiral element along the circumference has a housing wall which has an annular surface forming a fluid seal with the side plate of the opposing scroll member, the | Forming a spiral element into a housing * J 409881/1012 - 54 - 19. Device according to one or more of the preceding 5 Claims, characterized in that a separate Ge ■ home is provided that a fluid ι around the spiral elements volume forms, with the opening or openings assigned to the zone of lowest pressure being arranged in such a way that! one of the outer sections of the arch elements: Have a distance. 20. The apparatus of claim 13 and other of the preceding ί the claims, characterized in that the coupling ^; device has an overall square shape and is designed in such a way that it produces passages for connection to a line and openings which are assigned to the zone of highest pressure. 21. Device according to the preceding claims, characterized in i characterized in that the opposing spiral. elements (304, 305) are each provided with a shaft; the inlet line in one shaft and the outlet! line is formed in the other shaft (Fig. 15). ; 22. Device according to the preceding claims, characterized in that j, that between the drive device and the! a spiral element (30) describing a path; a mechanical connecting device which is flexible in the radial direction
(153, 248; 243) is arranged, which this device for
Generation of a centripetal radial force predetermined
Has size. 23. The device according to claim 22, characterized in that
the mechanical connecting device, which is flexible in the radial direction, has a device which has a
centripetal radial force results, which is smaller than that
Centrifugal force, the difference of these forces being the
radial sealing force results. - 55 - 409881/1012 24. The device according to claim 23, characterized in that the mechanical compliant in the radial direction Connecting device is designed to be pivotable (Fig. 31). 25. The device according to claim 23, characterized in that that the mechanical connecting device, which is flexible in the radial direction, has a sliding piece arrangement (Fig. 33). j 26. Device according to claims 24 and 25, thereby ge j indicates that this pivotable device [(248, 153) or this slide assembly (244) pressure | springs (161, 162; 186) for generating the centripetal force having. j 27. The device according to claim 22, characterized in that the mechanical flexible in the radial direction Connecting device is designed so that a centripetal force is generated, which is substantially is equal to the centrifugal force, with means for forming a separate adjustable radial Sealing force is provided. 28. Device according to claims 24 to 27, characterized in that that a counterweight (167, 190) is used to create a separate, adjustable radial sealing force in connection with the pivotable device (248, 153) provided with a compression spring or with a Compression spring provided slide assembly (244) is provided. 29. Device according to den.Ansprüche 22 to 28, characterized in that that the centrifugal force balancing device less than the total centrifugal force compensates and the unbalanced part of the centrifugal force the radial sealing force between the arch elements forms. 409881/1012 -56- 2A28228 30. The device according to claim 29, characterized in that the centrifugal force compensating device is designed as a compression spring or as a counterweight. 31. Device according to claims 22 to 28, characterized in that that the centrifugal force balancing means substantially all of the centrifugal force cancels and a device is provided which generates a separate controllable radial sealing force. 32. Apparatus according to claim 31, characterized in that that both devices are designed as compression springs or the former a counterweight and the device to generate a radial sealing force is a compression spring. 33. Device according to the preceding claims, characterized in that the axis of the pivotable device perpendicular to the radius of eccentricity of the spiral element describing a path or with this forms an angle that is smaller than 90 °. 34. Device according to the preceding claims, characterized in that the device for the axial Sealing in combination a device for applying a mechanical and a fluid force which results in a first axial force acting on the fixed spiral element, as well as the coupling device, which is arranged between the spiral element moving on a path and a housing part and counteracts this first axial force with a second axial force. 35. Apparatus according to claim 34, characterized in that the device applying a mechanical force is a wave-shaped spring washer. 409881/1012 36. Apparatus according to claim 34, characterized in that the device applying a fluid force Has fluid chamber from which fluid pressure is applied to the side plate of the fixed scroll member is, as well as a device for introducing high pressure fluid into this fluid chamber, from an outer Source or from the area of highest pressure in the device. 37. Device according to the preceding claims, characterized in that the coupling device has a Having ring between the side plate of the spiral element describing a path and a housing part, which has oppositely disposed keyways on each surface in which keys slide the are mounted on the side plate of the scroll moving element and the housing part. 38. Apparatus according to claim 37, characterized in that that on each side of the coupling ring lubricant grooves are formed which communicate with one another stand. 39. Apparatus according to claim 37, characterized in that the coupling device has rolling elements which are arranged so that the axes of the rolling elements! which rest on one side of the coupling ring, are perpendicular to the axis of the keyways on that face j. 40. Device according to the preceding claims, characterized in that a crank (246) for connection the main drive shaft is provided with the mechanical connecting device which is flexible in the radial direction. 41. Device according to the preceding claims, characterized marked that for reducing or eliminating 409881/1012 from vibration counterweights are attached to the crank. 42.Vorrichtung according to the preceding claims, characterized in that that the abutting end faces of the arch elements of the fixed spiral element are lubricant grooves exhibit. 43.A device according to the preceding claims, characterized in that that a fastening device (211) for fastening the fixed scroll element to the housing is provided which can be adjusted to adjust the angular orientation of the spiral element within the housing is. 409881/1012 Blank page