DE3346546A1 - SPIRAL MACHINE, SPIRAL PART FOR A SPIRAL MACHINE AND METHOD FOR MACHINING IT - Google Patents

Description

DESCRIPTION:

The invention relates to a spiral machine, a method for machining the flanks of spiral turns on the Spiral machine and spiral parts for the spiral machine.

man

By "spiral" machines is meant a class of machines which are capable of displacing various types of fluids to serve. Such devices can be designed as an expander, a displacement motor, a pump, a compressor, etc. will. Many features of the present invention are applicable to all of these types of machines. The following execution described for explanatory purposes examples relate to a compressor for gaseous fluids.

Generally speaking, a "scroll machine" includes two scroll wraps similar configuration, each mounted on a separate end plate and thus a spiral part form. The spiral parts are fitted into one another in such a way that one spiral turn has a rotational displacement of 180 opposite the other owns. The machine works when a spiral part (the "circling" spiral part) is opposite to the the other spiral part (the "fixed" spiral part) moves and there is a linear contact between the flanks of the corresponding turns takes place. This creates moving, isolated, crescent-shaped fluid pockets educated. The spirals are generally designed as involute circles. Ideally, there aren't any Relative rotation between the spiral parts during operation, i.e. the movement is entirely curvilinear Translation (i.e., no line in the body rotates). The fluid pockets guide the fluid from a first zone in the scroll machine where a fluid inlet is located to a second Zone in the machine where there is a fluid outlet

BAD ORIGINAL _21-

i / S * "

is located. The volume of the sealed pocket changes as it changes from the first to the second Zone moves. There are at least two sealed pockets at any one time. If there are multiple pairs of sealed There are pockets at a given time, each pair has a different volume. Located in a compressor the second zone is at a higher pressure than the first zone and is physically in the middle of the device appropriate; the first zone is then on the outer circumference of the machine.

Two types of contact form the fluid pockets, that arise between the spiral parts: axially running, tangential line contacts between the spiral surfaces the turns that are caused by radial forces ("flank sealing"), and surface contacts that by axial forces between the flat edge surfaces (the "tips") of each turn and the opposite end plate are generated ("tip seal"). In order to achieve a high degree of efficiency, both types of contact must be used a good seal can be achieved. However, the present invention is primarily concerned with flank sealing. In a conventional scroll compressor (i.e. one in which the flanks are circular involutes) to achieve a good flank seal, there is no relative rotation between the spiral parts.

In general, scroll machines are described in U.S. Patent 801,182. Representative subsequent patents which Describing scroll compressors and pumps are U.S. Patents 1,376,291, 2,475,247, 2,494,100, 2,809,779, 2,841,089, 3,560,119, 3,600,114, 3,802,809, 3,817,644, 3,884,599, 4,141,677, 4,300,875, 4,304,535 and 4,357,132.

BATH ORIGINAL

The spiral machine concept has been known for some time and has certain advantages. For example scroll machines have a high isentropic and volumetric efficiency and are therefore proportional to P small and light with a certain capacity.

They are quieter and more vibration-free than many compressors, as they do not use large reciprocating parts (e.g. pistons, connecting rods, etc.). Because all fluid flow is in one direction

, Q takes place, with a simultaneous compression in several opposite pockets takes place, there is less pressure-generated vibration. These machines have in addition, a high level of reliability and a long service life due to the relatively small number of movable devices Parts, the relatively low speed of movement between the spiral parts and due to an inherent insensitivity to fluid contamination. Still, the reason is why spiral machines are not widely used, presumably because these machines are difficult to manufacture and that inherent sealing and wear problems arise.

Particularly difficult when building spiral machines is the question of how a relative angular rotation between the Spiral parts, when one goes through an orbit with respect to the other, can be prevented. This question is relatively often released through the use of an Oldham coupling placed between the orbiting scroll part and located in a fixed area of the machine. An Oldham coupling includes an Oldham ring and two sets of wedge parts on sliding blocks. On one side of the Oldham ring grooves are formed, which are below right Make angles to similar grooves on the other side. One set of wedge parts is circling with a face Spiral part connected and located in the grooves

γ on one side of the Oldham ring, while the other set of wedge parts is attached to either the fixed scroll or the machine housing and is located in the grooves on the other side of the Oldham ring. The old

r-harn-ring moves back and forth parallel to the grooves,

which include the set of wedge members attached to the fixed scroll member or housing. on in this way the Oldham coupling acts as a device which prevents angular rotation of the orbiting scroll member controls (i.e. prevents) in opposite to the fixed spiral part, a concept which is considered essential for the correct function of a conventional spiral machine. U.S. Patent 4,121,438 shows such a machine.

However, scroll machines which make use of the Oldham coupling have problems in assembly, operation and disadvantages in maintenance. These are essentially based on the large number of parts which the coupling

2Q development. This large number of parts increases ax material, Manufacturing and assembly costs. The sliding blocks or the Wedge parts on the Oldham coupling also all slide in the grooves on the Oldham ring, creating lubrication and wear problems result. In addition, the ring going back and forth naturally cannot be balanced.

There are other devices that allow relative rotation can be prevented between the spiral parts. This includes multiple drives, which the two spiral parts around different centers drive and similar concepts. However, due to their complexity they also show these facilities have many undesirable features of the Oldham coupling.

γ With the present invention, the problem is attacked from a different direction. The basic concept of the invention consists in the use of a simple device controlling the rotation of the circling spiral part / which does not eliminate a relative rotation but sets it to a relatively small value, in combination with a slight modification of the contour of the spiral turns, whereby the limited relative rotation between the spiral parts is compensated so that between the

- ^ q fertilize the sealing flank contact maintained will. Three different versions of the rotation controlling device are described, one of which is simple connection is that between the orbiting scroll part and a fixed section of the compressor

• j ^ g lies. Two embodiments are "four-rod connections" and two additional embodiments relate to crank and slide assemblies. All versions couple the orbiting and the fixed spiral part in a certain angular relationship in all positions when the orbiting The spiral part revolves opposite the fixed spiral part.

The connection controlling the rotation of the orbiting scroll member according to the present invention has the disadvantages of the known institutions that exercise this function. Since it has fewer parts, it is they are cheaper to manufacture and much easier to assemble. The lubrication problems are also on a reduced to a minimum, since there are fewer connections and, in one embodiment, only pivot connections instead of sliding connections. In addition, the anti-rotation part does not include a reciprocating one Ring.

So that the slight twisting of the orbiting scroll part is possible, the present invention uses two special methods for modifying the spiral winding contours. Both processes are very easy to carry out and result in a highly effective flank seal (one method leads to a theoretically perfect flank seal) when used together with the one mentioned above Connection can be used. A new method of machining the turns is also described.

The compressor according to the invention also includes an improved drive device, which the movable scroll member moves in its orbit, is compact, and is also easy to manufacture and assemble. This drive device, of the two exemplary embodiments

are written, results in the necessary contact between the spiral turns, which leads to an effective winding seal while at the same time performing an automatic relief function when constipation or

2Q the like occurs. When a non-compressible fluid is sucked into the compressor, the orbital radius of the circling spiral part is automatically reduced, so that this fluid can escape into a zone of lower pressure between the spiral turns

2g (i.e. the spirals simply "ride" over any existing Liquid). This function is achieved and works without additional parts, for example valves or the like very soft. The drive device is housed within the upper crankshaft bearing and reduced to

QQ this way the axial dimension of the machine and reduces the vibrations.

Finally, the compressor according to the invention comprises an improved one Thrust bearing, with which the axial load of the kreisengpj the spiral part is added. The drawer store uses them

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inherent rotary movement of the revolving spiral part from and This creates a squeeze film, which forms the oil-bearing surface for the bearing. The resulting bearing shows significantly less friction than conventional needle roller bearings and

, - is considerably less susceptible to wear than conventional ones Ball-bearing. Ball thrust bearings, especially those with relatively small balls, have such high point loads that that they tend to wear out. The inventive The bearing is also relatively inexpensive, very simple in construction, and easy to manufacture and assemble.

Embodiments of the invention are based on the following the drawing explained in more detail; show it:

■ i c iig. 1 a vertical section through an invention !

proper refrigerant compressor;

Fig. 2 is a view of part of the top of the in Fig.1 shown compressor;

3 shows a section along line 3-3 in FIG. 1; 4 shows a section along line 4-4 in FIG. 1; 5 shows a section along line 5-5 in FIG. 4; 6 shows a section along line 6-6 in FIG. 1; 7 shows a partial section along line 7-7 in FIG. 6; Fig. 8 is an exaggerated, enlarged view of the orbiting drive device of Figure 6 in its normal drive position;

FIG. 9 is a view similar to FIG. 8, but in which the drive device is in its relieved position is shown;

10 shows a section along line 10-10 in FIG. 1; 11 shows a section along line 11-11 in FIG. 1;

Fig. 12 is a bottom plan view of the fixed upper scroll part; s

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13 shows the plan view of the lower, orbiting spiral part ;

14 is a view similar to FIG. 4, in which a second embodiment of the rotation kon

Trolling device according to the invention shown is;

15 is a horizontal partial section showing a third embodiment of the invention

shows the rotation control device;

16 is a view similar to FIG. 15, in which a fourth embodiment of the invention

moderate represents the device controlling the rotation;

Fig. 17 is a horizontal partial section in which a second embodiment of the fiction

according to the drive device is shown in its normal drive state;

FIG. 18 is a view similar to FIG. 15, but in which the drive device in its relieved to

stand is shown;

19 shows a schematic representation of an exemplary embodiment two cooperating scroll wraps according to the present invention;

20A, 20B, 21, 22 and 23 are diagrams of the inventive geometry showing the nomenclature used;
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24 shows the schematic view of a device with

which the machining method according to the invention can be carried out. -28-

In Fig. 1, a refrigerant compressor is shown as an example in a hermetically sealed design. The compressor is located within a hermetically sealed envelope, which consists of an upper shell 10 and a lower shell 12 consists. The shells are welded at 14 in the usual way. At the bottom of the lower shell 12 a plurality of feet 16 are attached, one of which is shown. The arrangement includes an engine 18 which is drivingly connected to a crankshaft 20. This in turn drives a scroll type compressor 22 connected to its upper end. An oil pump 24 is from the lower The end of the crankshaft 20 is driven and lubricates the machine, in the lower shell 12 there is a Lubricant sump, the upper level of which is denoted by 26.

The motor-compressor assembly includes a lower bearing housing 28 in which a bearing 30 is located. In this is the lower end of the crankshaft 20 is rotatably supported and supported. An upper bearing housing 32 in which there is a bore 33 is located with spaced-apart bearing sleeves 34 and 36, rotates and supports the upper end of the Crankshaft 20. The bearing housings are fastened to one another by means of a plurality of threaded bolts 38 which form the stator Pinch 40 of the motor 18 between them. On the crankshaft A rotor 42 is fastened to 20 and arranged within the central bore of the stator. The motor corresponds in each case Respect to conventional construction and function. The motor-compressor assembly is inside the lower shell 12 is mounted by means of a plurality of mounting bolts 44 (shown once) which are screwed into the lower bearing housing 28 and to the underside of the lower shell 12, as best seen at 46, are screwed. A leak out the shell is prevented by means of an O-ring 48, weleher engages tightly on the outer circumference of each mounting bolt 44.

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The compressor itself comprises an upper, fixed scroll part 50 and a lower, orbiting scroll part 52 with a flat lower surface 53 and a downwardly extending drive hub 54. This is within c an eccentrically arranged bore 56 in the upper end of the crankshaft 20. The end of the hub 54 has a recess 55. An upper counterweight 57 is provided near the bore 56 on the crankshaft 20 and supports it helps to balance the eccentricity of the drive. the

- ^ q crankshaft also has a lower counterweight 59, which is attached near its lower end and completes the balance system in a known manner. That fixed spiral part 50 is at a precisely determined distance above the planar upper surface 58 of the upper bearing

■ ^ 5 housing 32 arranged by means of a spacer ring 60 and screwed to the housing 32 with several bolts 62. The bolts 62 also serve to clamp the spacer ring 60. The upper end of each bolt 62 protrudes into a nylon spacer 64 which is located within a cup-like Element 66 is located. The latter is attached to a mounting ring 68 on the top of the upper Shell 10 is welded on. In this way the top of the motor-compressor assembly is at the top of the Shell attached. Only one such connection is shown; however, several are provided.

The fixed scroll member 50 includes a planar tip sealing surface 70, from which a spiral turn 72 protrudes. The spiral part 50 is provided with a centrally arranged, kidney-shaped dispensing opening 74 is provided, which is provided with a Communicates dispensing chamber 76, which is located on the top surface thereof. The chamber 76 is through a with a Valve plate 78 provided with a suitable seal, through which openings 79 extend. The valve plate 78 is held in place by a cylinder head 80 attached to the top surface of scroll 50 by means of

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a plurality of screws 82 is attached. The direction of flow through the openings 79 is by a conventional, sheet-like Check valve 81 controlled, which on the valve plate 78 together with the usual back disk 83 by means a rivet 85 is attached.

The expelled fluid passes from the cylinder head 80 via an opening 84 in which one end of a Äuslaßrohres 86 is arranged. The tube 86 extends over the top of the assembly down between the latter and the shell to a point where it comes out of the Shell exits in the normal manner (not shown). Suction gas is normally fed into the shell via a fitting 88 introduced, which extends through the wall of the upper shell 10. The motor compressor described here is of the so-called "low-side" type, in which suction gas located in the hermetically sealed shell to cool the engine, etc. The gas enters the compressor 22 on the circumference of the spiral turns.

Orbiting scroll 52 includes a planar tip seal surface 90, from which a spiral turn 92 protrudes. This touches the turn 72 in a relative Circular movement of the spiral parts in the usual way so that there are fluid pockets of decreasing volume form. The tips of the turns 92 should be close to the surface 70 of the fixed scroll member and the tips of the turn 72 should lie tightly against the surface 90 of the orbiting spiral part. The middle zone of the circling spiral part 52 is provided with a kidney shaped recess 94 which facilitates the flow of the outlet fluid will. Both spiral turns 72 and 92 taper equally and uniformly in cross-section, all the more so to their Root to maximize the strength of the spiral wrap. The outlet opening 74 and the recess 94 are configured in such a way that the maximum flow area results without the wor-

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to weaken zel of the neighboring spirals. The tip sealing surfaces 70 and 90 should lie in parallel planes which are parallel to those planes in which the The tips of both spiral windings lie and which are perpendicular to the axis of rotation of the crankshaft 20.

The drive device does not use a rigid coupling between the crankshaft and the orbiting spiral part but gives way radially, so that an automatic relief of the compressor is possible if incompressible fluid is drawn in or misalignment the parts occurs. The drive device keeps the flanks of the rotating spiral part in sealing contact to those of the fixed spiral part using centrifugal and driving forces. This is done in a axially very compact manner using a relief hub 100, as best shown in FIGS. 1 and 6 to 9 is shown.

The hub 100 includes an outer circular cylindrical holder 102 and axially spaced from one another inner bearing sleeves 104 and 106, in which the hub 54 of the orbiting spiral part is mounted. The holder 102 is provided on its periphery with a flat driven surface 108 which lies in a plane which is parallel to the axis of rotation of the crankshaft. The driven surface 108 is in driving communication with a complementary flat driving surface 110 in the wall of the bore 56, the latter surface having a greater width than the first. The bore 56 has the rest such a size and shape that there is limited relative tangential displacement between the hub 100 and the Crank 20 is possible. The center of rotation of the crankshaft is denoted by cc. One rotation of the crankshaft 20 causes the hub 100 to revolve around the axis cc.

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This in turn leads to the fact that the hub 54 and thus also the orbiting spiral part 52 revolve around the axis cc. Of the The radius of the circle of the orbiting spiral part is determined by the geometry of the spiral spiral profile (i.e.,

5, by touching the flanks of the turns of the circling Spiral part with the flanks of the turns of the fixed spiral part).

When the turns on incompressible fluid mass hit, the forces generated thereby, which seek to separate the windings, are passed through the relief hub 100

• ι recorded which from the normal drive position, the in FIGS. 6, 8 and 9 is shifted into the exaggerated position shown in FIG. To this In this way, the spiral turns can separate and pass over the incompressible fluid mass, whereupon centrifugal forces cause the circling spiral turn back into tight contact with the fixed spiral turn emotional.

The axial nesting of the parts minimizes the axial height of the arrangement. In addition, in this way the upper counterweight can be very close to the center of mass of the circling spiral part are arranged, what the bearing loads and bending forces on the crankshaft as well as the Reduced the size of the counterweight required. In addition, there is no cantilever drive bearing on top of the Crankshaft required, which further reduces bearing losses.

The rotating drive device described below enables the desired orbital movement and at the same time automatic unloading of the compressor when it encounters incompressible fluid. This embodiment, which in the horizontal section in FIGS. 17 and 18 includes a crankshaft (with the center of rotation cc), in the upper end

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33465Λ6

there is an axial bore 114 of the shape shown, det. The important part of this bore is a circular cylinder surface 115 (with the center cp) in which a hub 116 with a projection 117 is housed. The projection 117 has the same radius as the surface 115. The hub 116 has a circular bore 118 (central axis es), in which the hub 54 of the orbiting spiral part is mounted. Appropriate bearings can be found at the interface of bore 118 and hub 154 can be provided in case of need. As can be seen, the geometry is such that when the crankshaft 112 rotates about the axis cc, the centrifugal forces normally affect the corresponding parts hold in the positions shown in Fig. 17, in which the radius of the circular motion through the geometry the spiral winding flanks, as mentioned above, is determined. However, if a relief situation arises, it can Rotate the hub 116 about the center point cp into the position shown in FIG. 18. Here the Separate spiral winding flanks from one another to the extent necessary to overcome the intermediate incompressible ones Matter is necessary.

The coupling of the spiral parts to control the relative rotation taking place between them takes place to a great extent easy way. In the embodiment according to FIGS. 1 to 13 (cf. in particular FIGS. 1, 4 and 5) happens this in that a projection 120 is provided on the outer circumference of the orbiting spiral part 52, through which an axial bore 122 extends. In this there is pivotably a projection 124 at one end of a simple one Link 126, the opposite end of which is articulated to some fixed part of the device is. In the illustrated embodiment, the connecting member 126 is on one of the axially extending positioning pins 128 stored, which protrudes into the fixed scroll part 50 and the upper bearing housing 32 and this

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33Λ65Α6

Parts positioned exactly against each other. The lower surface of the link 126 is flat and slidably rests on the flat top surface of the spacer ring 60.

The link 126 is preferably as long as possible (to minimize the effect of the protrusion 124 moved on an arc instead of a straight line). It should be perpendicular to one as much as possible work imaginary line that runs between the center of the orbiting spiral part and the bore 122. These very simple connection arrangement replaces the complex Oldham coupling used in known devices will. The small amount of relative twist between the scroll members that occurs with this connection arrangement is possible, is precisely controlled and has a defined size and type, so that they are readily accepted without loss of function or efficiency. This is explained below.

in Other simple connection arrangements are / FIGS. 14th to 16 shown. The embodiment of Fig. 14 is almost with that according to FIGS. 1 to 13 identical, with the exception that the simple link is relatively is straight, as indicated at 130, and is mounted on a projection 132 at its fixed end is. This is mounted on a bracket 134 which is rigidly attached to the upper shell 10. The moving end of the connecting member 130 corresponds in all respects to that which was used for the previous exemplary embodiment has been described; the function of the two links is the same. These two connection arrangements are known to those skilled in the art as four-rod connections. The first "rod" of the link is the link 126 or 130, which extends from a fixed part of the structure to the circumference of the orbiting spiral part. The second "rod" of the connection is the imaginary

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nary link between the pivot point on the circumference the circling spiral part and the geometric center of the spiral part. The third "rod" is the imaginary link, which is between the geometric center of the spiral part and the center of the circular movement of the spiral part extends. The fourth "rod" is the fixed structure that extends from the fixed pivot point of the first "rod" runs to the fixed pivot point of the third "rod".

The exemplary embodiments of the device controlling the rotation, which are shown in FIGS. 15 and 16 are shown, are both of the same construction with a crank and slider. In the embodiment of Fig. 15 is a pre

I ^ jump 120 on the orbiting spiral part 52 is provided with a radially extending, elongated slot 136 in which a displaceable pin 138 is located. This is mounted on a bracket 140, which in turn is rigidly attached to the upper shell 10. In the exemplary embodiment of FIG. 16, a pin 142 is fastened to the projection 120 of the orbiting spiral part 52 and is arranged displaceably in a radially extending elongated slot 144 on a bracket 146. The clip 146 is attached to the upper shell 10. In the last two exemplary embodiments, the rotation of the orbiting spiral part due to the mutual engagement of pin 138 in slot 136 and pin 142 in slot 144 is prevented.

Thus, in all four embodiments, the rotation of the orbiting spiral part is prevented in that it is pivoted about a single, relatively fixed pivot point. The only notable difference between the assemblies is that in the four-bar linkage assemblies the only pivot point moves in a slightly curved path while at the two arrangements with crank and sliding device

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33Α6546

the relative movement of the pivot point takes place in a straight line. In addition, in the embodiment of Fig. 15, the imaginary link varies between the single pivot point and the geometric center of the revolving spiral part in the circular motion of the spiral part, while it is fixed in the other embodiments.

Dealing with high shear forces, which is an inherent property of spiral machines is a field that has given designers many problems. With the present Invention it was recognized that these thrust forces can be coped with using a bearing, which when carrying the thrust load through a squeeze film mechanism from the inherent imbalance of the circular

makes use of the spiral part. This camp shows very well ^! low friction, is very easy to manufacture, requires only flat finishing, has high rigidity and, due to the low relative speeds, suffers small 2Q shear losses. It also transfers the thrust forces directly to the frame of the device (ie, the upper bearing housing 32).

As best shown in FIGS. 1, 10 and 11 can be seen, 2g, the thrust bearing assembly comprises a relatively thin one Bearing 150 made of Teflon (PTFE) and lead-impregnated bronze or another suitable bearing material. It points to each other opposite, parallel surfaces and touches on its lower side the flat upper surface 58 of the obe-QQ Ren bearing housing 32 and on its upper side the flat surface 53 on the orbiting spiral part 52 slidable Relative movement between the bearing 150 and the spiral part 52 is prevented by means of a pin 152 which is in both Parts protrudes. There are no oil grooves on bearing 150; gg instead is the upper surface 58 of the housing 32 with two concentric grooves 154 and 156 are provided. The groove 156

^ 33465Λ6

is an oil supply groove and is via several channels 158 with Oil supplied. The channels 158 communicate via the housing 32 with the bore 33 in the zone between the bearing sleeves 34 and 36. The groove 154 is an oil drainage groove through which the oil via several channels 160 to the open crankcase which is formed by the housing 32 can be withdrawn. In this way the oil transfer into the suction gas entering the compressor is reduced. The surfaces 53 and 58 should be parallel to each other and perpendicular to the axis of rotation of the crankshaft 20.

The function of this bearing is presumably based on the fact that the orbiting spiral part inherently tilts a little or wobbles as it circles. This creates a circumferential Oil shaft that traverses the entire surface of the bearing at a speed equal to the speed of rotation the crankshaft is determined. If the motor is operated at 3600 rpm in this way, the relative axial speed can be reduced of the parts this shaft cross the entire surface of the bearing 150 and the surface 58 in a circular path at 3600 rpm. A conventional hydrodynamic bearing would probably not work properly as it is not an adequate one There is relative movement (i.e. insufficient tangential velocity) between the scroll and the housing.

This is because it is only a circular movement with a relatively small displacement.

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Since the bearing according to the invention uses a relatively large, flat surface, the surface loading is proportional small and therefore a long service life of the bearing possible.

The thrust forces that occur at the top of the orbiting spiral part are due to the axial meshing of the two spiral parts added. In particular, the contact of the winding tips on a spiral part with the

IQ pointed sealing surface on the other spiral part does this. The screws 62 compress the scroll parts axially and the fluid pressure generated by the function of the Compressor is generated, pushes them apart. To achieve a good tip seal, sufficient Axial forces exist which press the spiral parts together or keep them sufficiently close to one another. on the other hand friction and wear should be reduced as much as possible.

In the present compressor, the peak wear becomes controlled by the thickness of the end of the outer turn of each spiral portion, as best shown in Figs. 12 and 13 is enlarged considerably. It it is known that the outer flank of the outer 180 ° of each scroll wrap is not used in the compression cycle will. Use is made of this fact in the compressor according to the invention to regulate the peak wear. As can be seen in FIG. 12, approximately the last 180 ° of the turn 72 are thicker than the rest the turn that starts at 170 and ends at 172. This surface slides on surface 90 of the orbiting spiral part 52. Lubricating oil is supplied to the interface through a passage 174 in the orbiting scroll member 52, its on the other hand, oil is fed from a vertical channel 178, which is connected to the space between the bearing sleeves 104 and 106 communicates a radial channel 180 (Figs. 7 and 13).

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The outer end of the channel 176 is in the usual manner provided with a stopper. As shown in FIG. 13, the approximately last 180 ° of the turn 92 also have larger ones Thickness than the remainder of the turn starting at 182 and ending at 184. In addition, this is an extended winding section provided with an oil supply groove 185 which supplies oil from a channel 186 which communicates with the channel 176 will. Due to these relatively wide areas, the surface load is in the axial direction and thus ! Q the tip wear is reduced.

The corresponding parts of the machine are lubricated by means of an oil pump 24, which is mechanically operated by the The crankshaft is driven and the oil is under pressure from the oil sump at the bottom of the shell, which is designated as 200 is, pumps to all moving parts of the machine that require lubrication. The oil pump 24 is in accordance with known criteria of known construction. For example, it can be like them in US Pat. No. 4,331,420 or US Pat 43 31 421 is described, to which reference is made. The inlet to the pump is marked 202 and the outlet the pump takes place via a vertical oil channel 204, which extends up to the center of the crankshaft 20.

As best shown in FIGS. 1, 6 and 7, the upper end of the channel 204 communicates with a transverse channel 206 in the crankshaft, the opposite ends of which communicate with vertically extending channels 208 and 210. The radially outer end of the channel 206 and the upper ends of the channels 208 and 210 are in a conventional manner provided with a plug. The channel 208 communicates with a radially extending channel 212 that defines the space between the Bringing bearing sleeves 34 and 36 into communication with a supply of pressurized lubricating oil. The channel 210 commu-

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ned with a substantially radially extending channel 214, which in turn communicates with the interface of surfaces 108 and 110, as well as with a radial one Channel 216 in the hub 100, which the space between the bearing sleeves 104 and 106 in communication with the source below Pressurized lubricating oil brings. The lubricating oil is drawn from the space between the outer pair of bearing sleeves Thrust bearings via channel 158 as mentioned and from the space between the inner pair of bearing sleeves to the cooperating ones Spiral tip surfaces over channels 118, 178, 176, 174 and 186 as set out above.

Since the lower counterweight 59 is below the liquid level of the oil sump (due to the size of the Counterweight, which is used to balance the relatively large eccentric mass of the orbiting spiral part is required), precaution is taken against that. the rotating counterweight pumps oil, which is unnecessary Would consume energy. This is done in that a recess 220 is formed in the lower bearing housing 28, which comes very close to the outer surface of the counterweight 59 as it rotates. The outer perimeter of the chamber 220 communicates with an oil outlet line 222, which is extends radially outward and then upward between the housing and the shell. When starting the compressor the rotation of the counterweight 59 causes oil to be pumped from the chamber 220 via line 220 into the sump of the bowl will. In order to make this emptying of the chamber 220 of oil possible, the housing 28 is provided with a channel 224, which communicates at one end with the central portion of the chamber 220 and at the other end with a conduit 226, which runs up to above the oil level in the bottom of the sump, gas or steam can flow in via this line enter chamber 220 when the compressor is started allowing any oil to be drained therefrom.

Excess oil on the top and bottom of the inner

ORIGINAL

Bearing sleeves, on the top of the outer bearing sleeves and the inside of the thrust bearing is via channels 217 and pulled back to the crankcase.

Conventional scroll compressors with spiral contours that are involutes require a curvilinear translation between the fixed and moving scroll parts to maintain line-to-line flank contact is obtained. When the curvilinear anti-rotation device is replaced by the connection according to the invention that makes a slight pivoting of the orbiting spiral part possible, a device must be used which maintains the linear flank contact so that the efficiency is made as high as possible will. Two methods are described below for this purpose. The first is an involute displacement method; the second is an involute modification that leads to spiral flank profiles, which are not true involutes or circular involutes.

The flank leak distances (i.e., the distance between the coils of the scroll working together) are extraordinary small if the first method is used. The second method theoretically gives flank leak distances of value zero.

Generally speaking, scroll compressors use two or more scroll turns that are made up of the involute of a plane

generated
Geometry / and to be mounted on base plates. If a generating circle is used, its radius, the thickness of the spiral wrap, and the total number of turns are selected to provide the desired volumetric displacement and pressure ratio. If the spiral parts are twisted 180 ° and brought together so that the flanks and tips touch, pockets form. When a spiral part is in a curvilinear translation (no line rotates in the body) opposite the

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other spiral part is moved, then these pockets are sealed and move inward to the center or outwards towards the ends of the turns, depending on the direction of rotation. If there are more than one and a half working turns the fluid in the pockets is compressed or expanded. If the movement is a real one Curvilinear translation is a perfect flank seal (if irregularities in the involute disregards). Due to the relatively long sealing line of the flanks and tips, small Clearances lead to significantly reduced efficiencies. In contrast to the elimination of edge spacing, the avoidance of tip spacing is not the subject of the present invention.

To explain the background and with reference to FIG. 20A, the equations are given below which the Spiral involute profiles describe when the relative motion is a curvilinear translation and the relative rotary motion between the generating (x-y) axes of the spiral parts is 180 °:

R = C (1 + Ar - MT / C) ² ) x ¹ ^ ²
Ar = 'Ac + Pi / 2 = Ap - arc tan (Ap) 25

Where: R is the distance between the center of the base circle and the point on the spiral profile,

C is the radius of the generating base circle, Ar is the roll angle,

T is the thickness of the spiral turn M a logical modification factor; M = 1 for area S1 and M = O for area S2
35

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Ac is the numerical control angle that is in-

is incremented; it can also be thought of as the crank angle when between the the movable and the fixed spiral part are in contact at the observed point,

Ap is the polar coordinate angle.

Curvilinear translational motion requires the use of an anti-twist device, for example the complex and relatively oldham coupling. A much simpler and cheaper facility is the rotation controlling linkage described above. This arrangement enables however, a slight pivoting of the orbiting spiral part, which would normally lead to that the flanks of the spiral windings separate or interfere with each other and thus the efficiency of the machine to reduce. Because the geometry of the turn is changed, this distance or this mutual Interference can be reduced or eliminated. In this context, two profile modifications are explained below .

It has been discovered that conventional circular involutes can be used with the above-mentioned connection arrangement and an excellent flank seal is achieved if simply the internal involute profile of a spiral flank formed at a different base circle center point than the outer involute profile of the same winding flank will. The involute profiles are identical; however, the resulting turn varies in length along its length the thick. The base circles of both the inner and the outer flank can be on one or both spiral parts be moved. There are thus three possible cases: -44-

1. Only the inner and outer profile of the fixed Spiral part shifted against each other; 2. Only the inner and outer profile of the circling will be shown Shifted spiral part;

3. It will be the inner and outer profile on both Spiral parts shifted.

Surprisingly, it has been found that the above Case No. 1 on Best Poetry and Case No. 2 leads to the worst result. This finding is based on a theoretical analysis? presumably, however, in practice the leakage is that between working with each other Flanking occurs, also in case No. 2 acceptable. Two such, 'like turns 250 and 252, which matched one another are shown exaggerated in FIG. This is a machine similar to the case mentioned above No. 1, where coil 250 is the orbiting coil and coil 252 is the fixed coil and all of them Has corrections.

The geometry of the connecting mechanism according to the invention is shown in FIG. There mean:

P = location of the pivot point controlling the rotation on the revolving spiral part (for example the axis of projection 124),

es = location of the geometric center of the rotating spiral part,
cc = axis of rotation of the crankshaft, 3Ol = distance between the geometric center of the

orbiting spiral part and point P (i.e., the length of the imaginary link which formed by the circling spiral part), Am = relative angle between the spiral parts, β = angle from the starting point of the involute on the circular base circle to the center of the pivot pin (polar)

Υέ.

IE = eccentricity (radius of the circular movement of the circular Spiral part),

V = angular speed of the crankshaft, Tm = time,
S1 = inner flank profile,

S2 = outer flank profile.

In order to develop the spiral parts according to the invention, conventionally shaped spiral parts must first be constructed (as they would be used with an Oldham coupling) so as to achieve the correct displacement, the correct pressure ratio and to determine the exit opening geometry using conventional methods. This results in known ones Values for the involute base circle radius C, the winding thickness T and the number of windings on the outer surface. When this is done, the location of point P, the pivot point of the orbiting spiral part, must be selected. The distance between the geometric center es and the point P is L. The distance L is chosen as is convenient for manufacture. They can be smaller than that Distance between the geometric center of the spiral part to the outside of the spiral part, if the Pivot point P is located on the underside of the spiral part. However, it is preferably outside the outer turn, as shown in FIGS. 1, 4 and 13 shown. As the end of the outer Turn forms a convenient reference point, the pivot point P is chosen there for demonstration purposes, although any other point along the circumference of the spiral part would come into question. The length L represents the connecting link, which is formed by the orbiting spiral part between the center es and the pivot point P. The line between cc and es is referred to as the "center line".

As described above, it has been found that there are a number of basic interconnection mechanisms by which a only slight, controlled rotation between the spiral parts can be achieved. Because of the ease of the

-46-

Manufacturing, low cost, and easy lubrication, the four-bar linkage is preferred. If the Length L is sufficiently long and the link is substantially perpendicular to the line between FIG P and cc runs, the four-rod linkage movement is similar to the movement of the embodiment with The crank and slider of Fig. 16, since the point P moves substantially in a straight line and the Length L does not change. This embodiment is therefore the easiest to calculate. The others described Mechanisms follow a similar analysis with similar results.

The basic problem in Fig. 21 is that the orbiting scroll member twists through the angle Am when the center of the circling spiral part moves on the circular path with the eccentricity E. These corner excursions lead to a mismatch of the spiral surfaces, which at the same time leads to gaps and mutual interference at the Sealing points between the spiral flanks and thus leads to low capacity and low efficiency. the The size of the gap or the mutual obstruction depends on the size of the mismatch between the spiral surfaces from, which in turn depends on the connection geometry and depends on the spiral configuration.

Assuming that P is radially on a straight line through the center of the generating circle of the solid Spiral part moves, the value of Am is calculated as follows:

sin (Am) = E sin (VTm ) L

For small values of Am (which we are dealing with here) 5 is assumed:

Am = sin (Am) = E sin (VTm) (rad) ~ ⁴⁷ ~

Because the maximum angle by which the orbiting spiral part rotates with respect to the fixed spiral part, at VTm = 90 °, the following applies:

Am max = E / L (rad)

In Fig. 21, the value of Am is 0 ° when the center line intersects position a. There is thus a relative angle 0 between the scroll parts at this point, which means that there is no scroll face mismatch in this position gives. However, as the center line moves to point b, the value of Am increases to the value Am max, which leads to a maximum area mismatch. If one demands that the sealing points in the present inventive arrangement are at the same points as with an Oldham coupling (i.e. without allowable relative movement), then the profiles have to be modified for this. It was observed that at the positions a and c a relative angle of 0 ° lies between the spiral parts and therefore no radial correction is required. With the positions b and d, where the relative angle between the spiral parts has its maximum, the correction is maximum and equal

R max = [(E / L) / 2 (Pi) J 2 (Pi) C = EC / L 25

Between the points of correction 0 and the maximum correction, the radial correction has a mean value that is approximately same

(EC / L) sin (VTm)

Thus, when the uncorrected spiral parts are in the position that requires the maximum correction, a set of sealing points has a gap, which

-48-

to close requires correction while the other set of sealing points is actually in each other Is away. It has been discovered that these gaps and mutual interference can be corrected by adding the Involute profiles are moved in a direction perpendicular to a line through the spiral part centers and pivot point P is when the scroll members are in their untwisted position.

IQ If the correction or the shift is only to be applied to one spiral turn (cases No. 1 and 2), then the inner turn profile is shifted in a direction along the normal line by an amount / equal to R, whereby the gap is closed and the mutual interference is eliminated. The outer turn profile is shifted by the same amount in the opposite direction for the same reason.

If all four flank profiles are corrected (case no.3), then a similar correction is made to both spiral turns. If more precisely the inner profile of one Spiral winding is shifted in one direction along the normal line so that the gap is closed and the mutual one Disturbance is eliminated, then the outer profile of the same turn in the other direction is made of the same Reason postponed. The inner profile of the second spiral turn is also shifted, but in the opposite direction Senses like the inner profile on the first spiral turn; the outer profile is in the opposite direction shifted like the outer profile of the first spiral turn. The size of the correction applied to each winding flank in case No. 3 must be applied is as follows:

Fixed spiral winding Orbiting spiral winding Outer flank Right flank Outer flank Right flank

< ^Y >< ^R max>< ¹ " ^Y >< ^R max> ⁽¹ " ^{X) (R} max>

-49-

X is the proportion (% / 100) of the correction that is part of the outer flank of the fixed spiral wrap is desired, and Y is the proportion of the correction that is made on the inner Edge of the fixed spiral turn is desired. Thus, the correction on the outer flank results in the fixed Spiral plus the correction on the inner flank of the orbiting spiral total of R, as well as the combined corrections on the inner flank of the fixed spiral part and the outer flank of the orbiting one Spiral part.

The result is a spiral piece or two spiral pieces with a turn that is no longer of uniform thickness. In Fig. 19 it should be noted that the fixed spiral wrap 252 on which the entire correction is carried out has the same thickness wherever it intersects the x-axis and has a reduced thickness wherever it intersects the y-axis intersects below the x-axis, and has increased thickness wherever it crosses the y-axis above the x-axis cuts. Thus, as one moves inward along a corrected turn, the thickness changes continuously and has a maximum and minimum or "face value" approximately every 90 degrees. The result is that the Profiles in operation have such a shape and position that they come extremely close to one another and seal all necessary points at the necessary times.

As mentioned, the involute displacement method leads to a small edge distance or a small mutual distance Disturbance. The size of this distance or the mutual disturbance depends not only on the crank angle and the underlying spiral geometry, but also on the ratio K, i.e. the ratio of the modification, which was performed on the fixed spiral divided by the total modification. So if one assumes

-50-

that both spiral parts have been modified in the same way, K = 1 applies if the entire modification is assigned to the fixed spiral part; if, on the other hand, the entire modification is assigned to the movable spiral part, then K = O. Satisfactory compressors with a value of K = 0.5, originally believed to be the best, were manufactured and tested. However, a subsequent calculation surprisingly showed that the smallest error occurs when K = 1, while the IQ largest error occurs when K = 0. There is an almost linear relationship between the two, so the best value for K is 1 .K can also have values that are greater than 1 or less than 0, but these values have no known advantages.

As mentioned above, the same amount of correction need not be applied to each spiral portion. In case of unequal correction there are different values of K for different flank interfaces in the same machine. In the one here The terminology used represents the ratio K1 the K ratio for the fixed outer and the circular inner flank, the value K2 represents the K-ratio for the fixed inner and the circling outer flank. The optimal situation (the entire correction to the fixed spiral part) occurs when K1 = 1 and K2 = 1, which corresponds to the value K = 1.

Overall, the possible theoretical errors in the displacement method stem from three different causes: 30th

1) The sine error due to the approximation A = sin (A);

2) the bow defect of the link, if the length of the link is sufficiently large, it will be Errors very small, but usually this length limited due to practical dimensional considerations. This bug can be completely eliminated by using a crank and a slider can be eliminated.

-51-

3) The choice of the area to be corrected. When the shift is carried out completely on the movable scroll part, this error has its maximum value. Since there is no known benefit to this shift on the movable. To attach the spiral part, it should be attached to the fixed spiral part.

In practice, however, all these errors are probably so negligibly small that they do not adversely affect the compressor function IQ.

22 shows a flank contact between the outer, circling flank and the inner, fixed flank. These points are defined for each given geometric parameter (CTL) and for each compressor crank position (Ac). The additional material that must be added or removed from the involute profile for continuous contact between the spirals was determined according to the following equations:
20th

R = C (1 + Doc ² ) ¹ ^ ²

Doc = Ar + K1 (Am) fixed. outer spiral surface

Doc = Ar + (K2 - 1) Am mov. outer spiral surface Doc = Ar + K2 (Am) - T / C fixed inner spiral surface Doc = Ar + (K1 - 1) Am- T / C mov. inner spiral surface Ar = Ac + B + 5 (Pi) / 2 fixed outer spiral surface Ar = Ac + B + 5 (Pi) / 2 + Am mov. outer spiral surface Ar = Ac + B + 3 (Pi) / 2 fixed inner spiral surface Ar = Ac + B + 3 (Pi) / 2 + Am mov. inner spiral surface Ap = Ar - arctan (Doc)

In the case of a limiting link (four rods):

-52-

Am = B - Bb

Bb = (compare the calculation in steps 3-5 of the algorithm explained below)

For a holding sliding device (crank and sliding device with pin on the spiral part:

Am = aresin (JjE / lJsiri Ac))

K1 = modification size that corresponds to the outer flank of the

fixed spiral part is given, divided by the total modification between

the fixed outer and the movable inner flank.

K2 = modification size, which of the fixed inner

Spiral flank is given, divided by the 15th

Total modification between solid inner and

movable outer flank. Doc = "Dummy" variable
Ac = "crank angle", more correct than incremental angle

to watch.

B = angle from the start of the involute of an oribal base circle to the center of the pivot pin (Polar)

C = radius of the generating base circle _O1 _ T = thickness of the spiral winding

The increment Ac begins in such a way that Ar = 0. Nw = number of turns = (Ar until the end of the

Turn - Pi / 2) / 2 (Pi)
Stop if Ac = 2 (Pi) (Nw) + Pi / 2

_on In Cartesian coordinates:

ο 1/2
X = C (I + Doc ^) ' cos (Ar - aretan (Doc)) Y = C (1 + Doc ² ) ^1/2 sin (Ar - aretan (Doc))

With numerically controlled milling machines, the Cartesian coordinates must be programmed so that position coordinates One possible algorithm is as follows:

1. If involute profile = inner surface then Ac = - B - 3 (Pi) / 2 + Au

If involute profile = outer surface then

Ac = - B -5 (Pi) / 2 + Au
I ^ 2. If a restrictive sliding device (crank and sliding device with pin on the spiral part) is used, then the following applies:

Am = arc s in Qe / ils in (Ac)]

Go to step 7.

¹ ^ 3. If a constraining link (four-bar link) is used, then:

Xa = (E) cos (Ac + B + Pi)

Ya = (E) sin (Ac + B + Pi)

Xgb = Xa + (L) cos (B + Pi)

Xc = x-coordinate of the center of the projection 124 (Fig. 4) Yc = y-coordinate of the center of the projection 124 (Fig. 4)

Az = ((Xc-Xa) ² + (Yc-Ya) ² ) * ⁵

Yu = (Xa-Xc) / Az

Cc = arctan (Yu)
FH = F12 = 1

If (Ya - Yc)> 0 then go to step 4

Cc = 2 (pi) - Cc

FH = -1

g ₀ 4. Xum = Xc + Lik (cos (Cc))

If Xgb - Xum <10 then continue with step 5

F12 = -1

5. Yu = (Az ² + Lik ² -L ² ) / 2 (Az) (LIk) Cb = (FH) (F12) arctan (Yu)

Xb = Xc + Lik (cos (Cc + Cb))

Yb = Yc + Lik (sin (Co + Cb))
Xgb = Xb

Bb = arctan ((Xa - Xb) / L)

If Ya - Yb> 0 then continue with step 6

Bb = 2 (pi) - Bb

6. Am = B - Bb
7. Ar = Ac + B + 5 (pi) / 2 - Pi (LI) + Am (L2) Doc = Ar + K (Am) (L3) + (K-1) (Am) (L2) - (T / C) (CL1) R = C (1 + DOC) '

ρ = Ar - arctan (Doc)

X = ((R) cos (p) + [(TT) sin (Ar)} TT) L4! 5 Y = (R) sin (ρ) - [(TI) COS (Ar)] TT

8. Ac = Ac + Ai

9. If Ar = 2 (pi) (Nw) + P1 / 2 then go to m ± step 2 10. The process is complete.

NOMENCLATURE

E = eccentricity = C (Pi) - T

C = radius of the generating circle

L = distance between the geometric center of the ^ 5 circling spiral part and the center point P of the Connecting link pin

Ac = imaging angle

K1 = modification size which corresponds to the outer flank of the fixed spiral part, divided by the total modification between the fixed outer and movable inner flank,

K2 = modification size which corresponds to the inner flank of the fixed spiral part is given, divided by the total modification between solid inner and movable outer flank,

R = size of the pole vector
Ar = roll angle

Aro = roll angle (Ar) on the moving (circling)

Spiral part

Arf = roll angle (Ar) on the fixed part of the spiral B = angle from the beginning of an involute on the circling Base circle to the center of the trunnion

(Polar)

T = thickness of the spiral turn

Ai = increment angle (i.e. the angle incremented around the AC will)

Au = obtuse angle in Figure 20B (the angle between the x-axis and a line perpendicular to is a tangent on the generating base circle and through the contact points of the physical inner end of a turn and the involute curves from which its flanks are generated became)

T1 = tool radius

D = Distance between the base circle center and the center of an anchor pin

Lik = length of the twist control link (4 rods)
20th

Logical coefficients

Area: LJ L2 L3 L4 TT

Fixed inner 1 0 1 -1 -1 Fixed outer 0 0 1-1 1 Movable inner 110 1-1 Movable outer 0 10 11

The method of manufacturing the fixed and orbiting scroll parts with an NC machine or the like using the shifting method described above is shown schematically in FIG. Here poses represents a workpiece which is to be formed into a spiral winding. 302 is a holder that holds the workpiece 300 holds while this is done by a cutting tool tooth 304, which can be a face milling cutter,

-56-

"" 33A65A6

Ψ.

is processed. The machine that positions the cutting tool 304 with respect to the workpiece 300 is shown in FIG conventionally programmed so that from the common generating base circle of the involute spiral the

j- inner and outer flank profiles (identical curves) be shaped. When the workpiece is in one position in the holder for the entire flank machining is fixed, a conventional spiral winding of uniform thickness is generated, with both flanks evol ^ q venten are of the same base circle.

According to the invention, however, the outer flank of the turn is machined when the workpiece is in the position shown Position is in which it rests against a stop 308. The inner flank of the turn is processed when the workpiece is at the stop 306. Further changes are made to the orientation of the workpiece not. The distance between stops 306 and 308 is equal to the total displacement of the involute generating Base circle, which is required, calculated according to the criteria explained above for the above-mentioned displacement method, plus the total dimension of the workpiece between the stops. That is, the distance around which the workpiece moves from stop 308 to the stop

2g 306 moves is equal to the desired displacement of the generating base circles. The distribution of the correction component, which is given to each edge, is in turn determined by the base position (reference point) of the cutting tool 304 relative to the stops 306 and 308.

If the base position is in the middle, then the same correction is given to each edge.

Claims (6)

PATENT CLAIMS: ί 1. ) Spiral machine with a first scroll member having a spiral wrap; a second scroll member which has a second scroll turn and is mounted so that it is opposite to each other can move the first spiral part, wherein the second turn meshes with the first turn that when a movement of the second turn relative to the first turn along a certain path fluid pockets of progressively changing volume are formed, characterized in that the device, which for a movement of the second turn (92) takes care of the certain path includes: A drive device which has a first point on the second spiral part (52) on a substantially can move circular orbital path relative to the first spiral part (50); a rotation controlling device which restricts the rotation of the second scroll member (52) by it limits the movement of a second point to it. 2. Spiral machine according to claim 1, characterized in that the movement of the second point is essentially one straight path with respect to the first spiral part (50) is limited. 3. Spiral machine according to claim 2, characterized in that that the straight path runs essentially radially to the second spiral turn (92). 4. Spiral machine according to claim 2, characterized in that the straight path is slightly curved. 5. spiral machine according to claim 2, characterized in that that the straight path is a really straight line. 6. Spiral machine according to one of claims 1 to 5, characterized in that the first point is in the middle of the second spiral turn (92) is located. 7. Spiral machine according to one of claims 1 to 6, characterized in that the second point is radially outside the second spiral turn (92) is located. 8. Spiral machine according to one of claims 1 to 7, characterized characterized in that each spiral turn (72,92) has an inner and an outer flank, the profile of which is the involute of a circle is. 9. Spiral machine according to one of claims 1 to 7, characterized in that each spiral turn (72,92) has an inner and has an outer flank, the profile of which is the involute of a planar geometrical figure. 10.Spiral machine according to claim 9, characterized in that that the center of the generating figure of the involute profile on the outer flank of both turns (72, 92) opposite the center of the generating figure of the involute profile of the inner flank of the same turn (72,92) is offset. 11.Spiral machine according to claim 9, characterized in that that the center of the generating figure of the involute profile of the outer flank of a turn (72,92) opposite offset from the center of the generating figure of the involute profile of the inner flank of the same turn (72,92) will. ¹ ORIGINAL BATHROOM 12 = spiral machine according to claim 11, characterized in that that the device controlling the rotation with the second spiral part (52) essentially on a single one Point and that the centers are offset from one another substantially along a line that is normal stands on a line, which between said single point and the center of the second turn (92) runs when the spiral parts (50,52) are not twisted relative to each other = 13 = spiral machine according to claim 12, characterized in that that the geometrical figures are circles of equal radius, and that the centers of one another at each turn (72,92) are offset by an amount equal to EC / L, where is E = radius of the circular movement C = radius of the generating base circle L = Distance from the geometric center of the winding turn (92) up to the second point = 14 = spiral machine according to one of the preceding claims, characterized in that the rotation controlling means comprises a link (126) which coincides with one section is articulated to the second spiral part (52) and is thus mounted to another section is that it can rotate about an axis, which is fixed with respect to the first spiral part (50). 15 = spiral machine according to claim 14, characterized in that that the axis of the connecting link (126) which runs between the connecting link sections is substantially perpendicular to a radius of the second turn (92) formed by the articulation of the link (126) runs with the second spiral part (52). BAD ORIGINAU 16. Spiral machine according to claim 14 or 15, characterized in that that the articulation of the connecting member (126) with the second spiral part (52) extends radially is outside the second turn (92). 17. Spiral machine according to one of claims 14, 15 or 16, characterized in that the other portion of the link (126) is mounted on the first scroll member (50) is. 18. Spiral machine according to one of claims 14, 15 or 16, which is arranged in a hermetically sealed shell, characterized in that the other section of the connecting member (126) is mounted on the shell (10,12). 19. Spiral machine according to one of the preceding claims, characterized in that the end that controls the rotation Means comprises a "four-rod link" (126,130) which the movable scroll member (52) with a solid support structure connects. 20. Spiral machine according to one of the preceding claims, characterized in that the rotation controlling Apparatus comprises a crank and slide mechanism which connects the movable scroll member (52) with a fixed one Support structure connects. 21. Spiral machine according to one of the preceding claims, characterized in that it has a crankshaft (20) which is rotated about a first axis and has a substantially flat drive surface (110), those in a plane perpendicular to a radius from the first axis and at a distance therefrom, wherein a drive element (102) with a substantially flat driven surface (108) in drive contact BATH ORIGINAL with the driving surface (110) and a driven Device (100) connected to the drive element (104) in an articulated manner on the second spiral part (52) is so that it can rotate relative to this about a second axis, which is one of the first axis Has a distance, whereby a rotation of the crankshaft (20) causes a circular movement of the second axis the second spiral part (52) opposite the first spiral part (50) about the first axis. 22. Spiral machine according to claim 21, characterized in that that the plane of the driving surface (110) is substantially parallel to a plane passing through the two Axes runs 23 "Spiral machine according to claim 21 or 22, characterized in that the drive element (102) is free can move on the driving surface, if an obstacle temporarily the second spiral part (52) on it prevents it from following its normal path of movement. 24o spiral machine according to one of claims 21, 22 or 23, characterized in that the drive element (102) is substantially annular in cross section. 25th 25. Spiral machine according to one of claims 21, 22, 23 or 24, characterized in that the drive element (102) is essentially cylindrical and that the driven surface (110) is on its outer circumference « 6 «, spiral machine according to one of the preceding claims, characterized in that the first spiral member (50) has a first flat sealing surface (70) and the first spiral wrap (72) has a first flat tip surface; the second spiral part (52) a second flat sealing surface (90) and the second spiral turn (92) a has second flat tip surface; the second spiral part (52) is mounted so that it moves with respect to the first spiral part (50), wherein the second turn (92) meshes with the first turn (72) such that when the second ^ O turn (92) opposite the first turn (72) along a certain way the inner and outer flanks of a considerable section of each turn (72,92) contact and form fluid pockets of progressively changing volume; with the first tip surface in sealing engagement the second sealing surface (90) and the second tip surface in close contact with the first sealing surface (70) is and so seals the bags; each turn (72,92) being arranged so that the outer flank at the outer end portion is the flank of the other Turn (92,72) not touched, the end portion of each turn (72,92) in the radial direction is substantially thicker than the rest, so that it is a disproportionately large proportion of the axial load on the Spiral parts (50,52) carries. 27. Spiral machine according to claim 2 6 ,. characterized in that it has an oil supply groove (185) in a tip surface and a device (186,176) with which oil is brought into the groove to reduce friction will. BATH ORIGINAL 2 8 »spiral machine according to claim 2 6 or 27, characterized in that that it comprises a device which lubricates at least one sealing surface (70.90) in a Zone where it is touched by a tip surface. 29. Spiral machine according to one of claims 26, 27 or 28, characterized in that at least one of the End portions extending over approximately 180 °. 30. Spiral machine according to one of the preceding claims, characterized in that it comprises: A solid support structure (32) which carries the first scroll member (50); a thrust bearing (150) which is arranged between the fixed support structure (32) and the second spiral part (52) and is substantially annular in plan view and is parallel, flat, uninterrupted Has bearing surface which points to the fixed support structure (10,12); a lubricator (154,156) which oil to the interface between the thrust bearing (150) and the provides a solid support structure (32) and creates an oil film between these parts, the resulting, small tumbling of the second spiral part (52) in its circular movement opposite the first spiral part (50) a "squeeze film phenomenon" between the thrust bearing (150) and the fixed support structure generated. 31. Spiral machine according to claim 30, characterized in that that the thrust bearing (150) is attached to the second spiral part. 32. Spiral machine according to one of the preceding claims, characterized in that it comprises: A driven crankshaft (20) rotating around a first axis and a cylindrical driving shaft Has surface, the flow axis of which is parallel to the first axis; a drive element (1Ö2), which has a cylindrical having driven surface which is in driving engagement with the driving surface; a driven device on the second spiral part (52) which is articulated with the drive element (102) is connected so that it rotates relative to this about a third axis which is a distance from the first Has axis and runs parallel to this, whereby a rotation of the crankshaft (20) leads to that the third axis on the second spiral part (52) relative to the first spiral part (50) about the first axis circles. 33. Spiral machine according to claim 32, characterized in that the axis of curvature of the driving surface is a distance from the first axis. 34. Spiral machine according to claim 32 or 33, characterized in that that the axis of curvature of the driving surface is at a distance from the third axis. BATH ORIGINAL 35. Spiral machine according to one of claims 32 to 34, characterized characterized in that the driving and driven surfaces have a common axis of curvature. 36. Spiral machine according to one of claims 32 to 35, characterized in that the first axis is a greater distance from the axis of curvature than the third Owns axis. 37. Spiral machine according to one of claims 32 to 36, characterized in that the axis of curvature is a Distance from the plane formed by the first and third axes. 38. Spiral machine according to one of claims 32 to 38, characterized in that the drive element (102) can rotate freely around the axis of curvature with respect to the crankshaft (20) if an obstacle occurs at times prevents the second spiral part (52) from following its normal path of movement. 39. Spiral machine according to one of claims 32 to 38, characterized characterized in that the drive element (102) is substantially annular in cross section. 40. Spiral machine according to one of the preceding claims, characterized in that the profiles of the inner and the outer flank of the first turn (72) is each involute of the same generating geometric figure are; the center of the generating figure of the profile of the outer flank of the first turn (72) a distance from the center of the generating figure of the profile of the inner flank of the first turn (72) has. 41. Process for the mechanical production of the inner and outer flanks of a spiral part from a workpiece using a programmable machine in which the profile of each flank from the same flat geometric figure is generated, characterized by the following steps: (1) The machine is programmed to base the inner and outer flanks of the spiral (72,92) machined on a generating figure located at a fixed point in relation to the workpiece; (2) The reference point is determined at which the workpiece is arranged opposite the cutting tool of the machine must be so that the spiral flanks are machined in accordance with the program; (3) The workpiece is positioned relative to the cutting tool in a first position that is a distance apart from the reference point and the workpiece is machined in such a way that one flank of the spirals (72, 92) results; (4) The workpiece is arranged in a second position relative to the cutting tool and processed in such a way that that the other flank of the spiral (72,92) results, wherein steps (3) and (4) follow steps (1) and (2) and can be in any order. 30th 42. The method according to claim 41, characterized in that the second position is a distance from the first position owns. BATH ORIGINAL 43. The method according to claim 41, characterized in that the first position is a distance in one direction from the reference point and that the second position is a distance from the reference point in the opposite Direction owns. 44. The method according to any one of claims 41 to 43, characterized characterized in that the first and second positions are substantially the same distance from the reference point "Own LQ. 45. The method according to claim 41, characterized in that the second position is at the reference point. 2g 46. The method according to any one of claims 41 to 45, characterized characterized in that the geometric figure is a circle. 47. The method according to any one of claims 41 to 46, characterized in that the profiles are circular involutes. 48. Fixed scroll member and movable scroll member for a scroll machine, wherein a portion of the movable Spiral part opposite to the fixed spiral part with an eccentricity E circles and where on movable scroll member a rotation controlling device is fixed at a point P and both Spiral parts contain a spiral turn, the inner and outer surfaces of which are on a generating circle based, characterized in that the inner and outer surfaces are represented by the following equations (Cartesian Coordinates) are defined: X = C (1 + Doc) ¹ ' ² cos (Ar - arctan (Doc)) Y = C (I + Doc ² ) ¹ ^ ² sin (Ar - arctan (Doc)) there are: 2 1/2
R = Cd + Doc) '- Doc = Ar + K1 (Am) fixed outer spiral surface Doc = Ar + (K2 - 1) Am movable outer spiral surface Doc = Ar + K2 (Am) - T / C fixed inner spiral surface Doc = Ar + (K1 - 1) Am- T / C movable inner spiral surface Ar = Ac + B + 5 (Pi) / 2 fixed outer spiral surface Ar = Ac + B + 5 (Pi) / 2 + Am movable outer Spiral surface Ar = Ac + B + 3 (Pi) / 2 fixed inner spiral surface Ar = Ac + B + 3 (Pi) / 2 + Am movable inner Coil spring Ap = Ar - arctan (Doc)
15th Am = aresin (LE / L] sin (Ac)) K1 = modification, which of the fixed outer Spiral flank is given divided by the total modification between solid outer and movable inner flank. firm K2 = modification, which the / inner flank of the Spiral part is given divided by the total modification between solid inner and movable outer flank. Doc = "Dummy" variable Ac = mapping increment angle B = angle between the beginning of the involute on the peripheral base circle to pivot _on pin center (Polar). C = radius of the generating base circle T = thickness of the spiral turn
E = C (Pi) - T L = distance between the geometric center of the revolving spiral part (52) and the Center point P of the connecting link pin, Ac is incremented starting with a value Ac such that Ar = 0,
Nw = number of turns = (Ar to the end of the spiral - Pi / 2) / 2 (Pi), stop when Ac = 2 (Pi) (Nw) + Pi / 2. 49. spiral parts according to claim 48, characterized in that it has a crank and sliding connection which between the fixed spiral part (50) and the movable spiral part (52) and a relative rotation the spiral parts (50,52) limited to a limited, specific value. 50. Fixed scroll part and movable scroll part for a scroll machine, with a portion of the movable scroll member opposite to the fixed scroll member an eccentricity E and a rotation controlling device at a point P on the movable scroll member is attached, each spiral part having a spiral winding with an inner and an outer surface, which is based on a generating circle, characterized in that the inner and outer surfaces are defined by the following equations (Cartesian coordinates):
25th X = C (1 + Doc ² ) ¹ ' ² cos (Ar - arctan (Doc)) Y = Cd + Doc ² ) ¹ ^ ² sin (Ar - arctan (Doc)) there are:
30th R = C (I + Doc) ' Doc = Ar + K1 (Am) fixed outer spiral surface Doc = Ar + (K # - 1) Am movable outer spiral surface Doc = Ar + K2 (Am) - T / C fixed inner spiral surface Doc = Ar + (K1 - 1) Am - T / C movable inner spiral surface 14th Ar = Ac + B + 5 (Pi) / 2 fixed outer spiral surface Ar = Ac + B + 5 (Pi) / 2 + Am movable outer spiral surface Ar = Ac + B + 3 (Pi) / 2 fixed inner spiral surface Ar = Ac + B + 3 (Pi) / 2 + Am movable inner spiral surface Ap = Ar - arctan (Doc) Calculation of Am:
(1) Xa = (E) cos (Ac + B + Pi)
Ya = (E) sin (Ac + B + Pi) Xgb = Xa + (L) cos (B + Pi)
Xc = x-coordinate from point P Yc = y-coordinate from point P Az = ((Xc- Xa) ² + (Yc - Ya) ² ) " ⁵ Yu = (Xa - Xc) / Az Cc = arctan (Yu)
FH = F12 = 1 If (Ya - Yc)> 0 then go to step 2 Cc = 2 (pi) - Cc FH = -1 (2) Xum = Xc + Lik (cos (Cc)) If Xgb - Xum <- 0 then continue with step 3 F12 = -1 (3) Yu = (Az ² + Lik ² -L ² ) / 2 (Az) (Lik) Cb = (FH) (F12) arctan (Yu)
Xb = Xc + Lik (cos (Cc + Cb))
Yb = Yc + Lik (sin (Cc + Cb))
Xgb = Xb Bb = arctan ((Xa - Xb) / L) If Ya - Yb> 0 then go to step 4 Bb = 2 (pi) - Bb
(4) Am = B - Bb
-15- K1 = modification of the fixed outer spiral flank divided by the total modification between fixed outer and movable inner flank, K2 = modification of the fixed inner spiral flank is given divided by the Overall modification between fixed inner and movable outer flank, Doc = "Dummy" variable Ac = mapping increment angle B = angle from the beginning of the involute on the circumferential base circle to the center of the Trunnion (polar), C = radius of the generating base circle, T = thickness of the spiral turn, E = C (Pi) - T ¹ ^ L = distance between the geometric center the orbiting spiral part (52) and the center point P of the connecting link pin, Ac is incremented starting with a value Ac, where Ar = 0, Nw = number of turns = (Ar to the end of the Spiral - Pi2) / 2 (Pi)
Stop if Ac = 2 (Pi) (Nw) + Pi / 2. 51. spiral parts according to claim 50, characterized in that they also comprise a four-rod connection, which lies between the fixed spiral part (50) and the movable spiral part (52) and a relative rotation the spiral parts (50,52) limited to a limited, specific value. 52. Fixed scroll member and movable scroll member for a scroll machine, wherein a portion of the movable Spiral part opposite to the fixed spiral part with an eccentricity E circles and on the movable Spiral part a connection that controls the rotation - 1 6 - member is fixed at a point P, each spiral part containing a spiral turn, the inner and outer surface based on a generating circle, characterized in that the inner and the outer Surface has a contour which is formed by an NC machine according to the following routine: 1. If involute profile = inner surface, then Ac = -B- 3 (Pi) / 2 + Au If involute profile = outer surface, then Ac = - B - 5 (Pi) / 2 + Au 2. Xa = (E) cos (Ac + B + Pi)
Ya = (E) sin (Ac + B + Pi)
Xgb = Xa + (L) cos (B + Pi) Xc = x-coordinate of point P. Yc = y-coordinate of point P. Az = ((Xc-Xa) ² + (Yc-Ya) ² ) * ⁵ Yu = (Xa-Xc) / Az Cc = arctan (Yu)
_{pl1 =} p ₁₂ _ -j If (Ya - Yc)> O then go to step 3 Cc = 2 (pi) - Cc
FH = -1 3. Xum = Xc + Lik (cos (Cc)) If Xgb - Xüm <0 then continue with step 4 F12 = -1 4. Yu = (Az ² + Lik ² -L ² ) / 2 (Az) (Lik) Cb = (FH) (F12) arctan (Yu) Xb = Xc + Lik (cos (Cc + Cb)) Yb = Yc + Lik (sin (Cc + Cb)) Xgb = Xb Bb = arctan ((Xa - Sb) / L)
If Ya - Yb > 0 then go to step 5 Bb = 2 (pi) - Bb -17- 5. Am = B - Bb 6. Ar = Ac + B + 5 (Pi) / 2 - Pi (LI) + Am (L2) Doc = Ar + K (Am) (L3) + (Κ-1) (Am) (L2 ') - (T / C) (L1) R = Cd + Doc ² ) ^1/2
ρ = Ar - arctan (Doc) X = ((R) cos (p) + Q (T1) sin (Ar)] TT) L4 Y = (R) sin (p) - C (TI) COs (Ar)] TT 7. Ac = Ac + Ai 8. If Ar = 2 (pi) (Nw) + Pi / 2 then go to step 9. The procedure is complete there are: E = eccentricity = C (Pi) - T
C = radius of the generating circle ¹ ^ L = distance between the geometric center of the orbiting spiral part (52) and the center T of the connecting link pin
Ac = imaging angle K1 = modification, which of the fixed outer spiral edge is given, divided by the total modification between fixed outer and movable inner flank K2 = modification of the fixed inner spiral flank divided by the total modification between inner and movable outer flank R = size of the polar vector Ar = roll angle Aro = roll angle (Ar) on the moving (orbiting) spiral part Arf = roll angle (Ar) on the fixed spiral part B = angle between the beginning of the involute on the circumferential Base circle to the center of the pivot pin (polar) T = thickness of the spiral turn -18- Ai = increment angle (i.e., the angle at which the AC in- is incremented)
Au = cone angle (the angle between the x-axis and a line that is perpendicular to a tangent to the generating base circle and passes through the contact points of the physical inner end of a coil and the involute curves from which its flanks were generated) T1 = Tool radius D = Distance between the center of the base circle and the center of the anchor pin Lik = length of the link controlling the rotation
where the logical coefficients are: Area: L1 L2 L3 L4 TT Fixed inner 1 0 1 -1 -1 Fixed outer 0 0 1 -1 1 Movable inner 1 1 0 1 -1 Movable outer 0 1 0 1 1 53. spiral parts according to claim 52, characterized in that they comprise a four-rod connection which between the fixed spiral part (50) and the movable 25 chen spiral part (52) and a relative rotation between the spiral parts (50,52) to a limited, limited certain value. 54. Fixed scroll part and movable scroll part 30th for a spiral machine, with a section of the movable spiral part opposite the fixed spiral part revolves with an eccentricity E and a connecting member controlling the rotation on the movable spiral part is fixed at a point P, each spiral part 35 contains a spiral winding, the inner and outer -19- surface based on a generating circle, characterized in that the inner and outer surfaces are one Have a contour that was formed by an NC machine according to the following routine: 1. If involute profile = inner surface then Ac = - B - 3 (pi) / 2 + Au If involute profile = outer surface then Ac = - B - 5 (pi) / 2 + Au 2. Am = aresin t (E / L) sin (Ac)} 3. Ar = Ac + B + 5 (Pi) / 2 - Pi (LI) + Am (L2) Doc = Ar + K (Am) (L3) + (K-1) (Am) (L2) - (T / C) (L1) R = C (1 + Doc ² ) ¹ ^ ²
ρ = Ar - arctan (Doc) X = ((R) cos (p) + [(T1) sin (Ar)] TT) L4 Y = (R) sin (p) - Qt 1) cos (Ar) I [TT 4. Ac = Ac + Ai 5. If Ar = 2 (pi) (Nw) + Pi / 2 then go to step 2 6. The procedure is complete. Are; E = eccentricity = C (Pi) - T C = radius of the generating circle ° L = distance between the geometric center the orbiting spiral part (52) and the center point P of the connecting link pin, Ac = imaging angle K1 = modification, which of the fixed outer spiral flank is given, divided by the total modification between fixed outer and movable inner flank, K2 = modification of the fixed inner spiral flank is given divided by the total modification between fixed inner and movable outer flank, -20- 33A6Ö46 R = size of the polar vector
Ar = roll angle
Aro = roll angle (Ar) on the moving (orbiting) spiral part
Arf = roll angle (Ar) on the fixed spiral part B = angle from the start of the involute on the circumferential base circle to the center of the pivot pin (Polar) T = thickness of the spiral turn
IQ Ai = Increment Angle (ie, the angle at which the AC is incremented) Au = cone angle (the angle between the x-axis and a line which is perpendicular to a tangent to the generating Baiskreis and approximate points by the contact-IQ of the inner end pyhsikalischen a turn and the involute curves from which the flanks were generated) T1 = tool radius D = distance between the center of the base circle and the center of the anchor pin
where the logical coefficients are: Area: L1 L2 L3 L4 TT Fixed inner 1 0 1 -1 -1 Fixed outer 0 0 1 -1 1 Movable inner 1 1 0 1 -1 Movable outer 0 1 0 1 1 55. spiral parts according to claim 54, characterized in that that they comprise a crank and slide connector, which is located between the fixed scroll member (50) and the movable scroll member (52) and a relative _OI _ rotation of these spiral elements (50,52) confined to a limited, specific value.