DE19603110A1 - compressor - Google Patents

Abstract

The aim is to improve a compressor comprising the following elements: a helical compressor with a first compressor element and a second compressor element whose helical ribs in the form of circle involutes engage with one another and can move relative to one another in an orbital movement about an axis, a medium to be compressed being taken in on the inlet side, successively compressed in chambers formed between the compressor elements and discharged on the outlet side; a drive motor; and a cam driven by the drive motor for producing the orbital motion of one of the compressor elements, a radial and an axial sealing force being generated between the compressor elements. The improvement is such as to maximise the isentropic total efficiency. To achieve this, it is proposed that a sealing force-generating unit producing the radial sealing force relative to the axis should be provided between the cam and orbiting compressor element, its pressure chamber acted on by a pressurised medium kept under a pressure which is proportional to the outlet-side pressure of the medium to be compressed.

Description

The invention relates to a compressor, comprising a Scroll compressor with a first compressor body and a second compressor body, whose in the form of a circular involute trained spiral ribs mesh and relative to each other move each other in an orbital motion are bar, with a medium to be compressed on the inlet side sucked in, formed between the compressor bodies Chambers successively compressed and released on the output side is driven by a drive motor and one by the drive motor eccentric to generate the orbiting movement of a the compressor body, being between the compressor bodies a radial and an axial sealing force acts.

Such compressors are known, for example, from US-A- 4,781,549 or CN-A-2,063,232 or 2,060,807.

With these compressors there is generally a problem with the Ab seal between the compressor bodies, these problems especially in the case of Be conditions, especially with large pressure ratios preferably at pressure ratios greater than about 5 to for example, about 20.  

A deterioration in the seal between the Ver chambers formed by the body of the poet lower the Volume capacity of the scroll compressor, however, has an Er Increasing the required for driving the scroll compressor Lichen and to be brought up by the drive motor performance.

For this reason, the isentropic total in particular decreases efficiency of such compressors.

The invention is therefore based on the object Compressor of the generic type to improve such that the overall isentropic efficiency is as high as possible.

This task is at the beginning of a compressor Written type solved according to the invention in that between the eccentric and the orbiting compressor body Sealing force generating radial sealing force to the axis Unit is provided in the pressure chamber, a pressure medium which acts under a to the output pressure of the compressing medium proportional pressure is available.

The solution according to the invention thus used to generate the radial sealing force not only due to inertia force of the orbiting compressor body, such as this is known from the prior art, but he it is possible through the sealing force generating unit, a defined, for the output pressure of the scroll compressor to generate proportional additional radial sealing force.  

This solution has, in addition to the fact that a far higher one Sealing force can be generated than is reasonable Masses of the orbiting compressor body through the Inertia is possible, yet another advantage that the additional radial sealing force regardless of the Rotation frequency of the orbiting movement is, in Contrary to the use of the prior art known inertia.

A particularly advantageous solution provides that the Sealing force generating unit with the eccentric around the axis co-rotates. This solution has the great advantage that can be ensured that the of the sealing force sealing unit generated exactly in the desired Direction works because there is a possibility that we direction of the generated by the sealing force generating unit sealing force exactly relative to the direction of the eccentricity align.

In the simplest case, the radial sealing force works exactly in Direction of the eccentricity of the eccentric relative to the axis. In the solution according to the invention, however, it is also possible to the direction of the sealing force relative to the direction of the eccentric Tricity deviating from this to determine if necessary additional forces acting between the compressor bodies To take into account.  

A particularly advantageous variant of the invention Solution provides that the sealing force generating unit as Double cylinder with two opposing pressure chambers is formed and that in one of the pressure chambers pressure acting on the outlet side pressure and in which others a reference print.

This solution opens up the possibility of not just printing in a pressure chamber as proportional to the outlet pressure Define pressure, but also the possibility ability to set the reference pressure exactly in order to achieve the Pressure difference in the two opposing pressures do not allow any defined sealing force subject to rivers, as is the case for example would be if no clear reference print is available would stand.

A particularly advantageous solution provides that the Refe pressure is a pressure proportional to the inlet pressure is. With this solution, the radial sealing force in particularly suitable to that of the seal between the Compressor bodies counteracting pressures, namely from pressure on the outlet side and the pressure on the inlet side, in ideally adapt, since the sealing force through both one for the input side pressure as well as for the output side pressure is defined proportional pressure and thus itself always set so that the pressure from an Ab seal fully counteracts forces.  

The sealing force generating unit can in principle in be trained in a variety of ways. A special one advantageous embodiment provides that the sealing power generation unit an inner body and one Has outer body that is displaceable relative to each other and one of which is non-rotatable on the eccentric pin sits.

Preferably, the sealing force generating unit comprises an inner body and one in one direction this displaceable outer body, the inner body sits non-rotatably on the eccentric pin. With this solution leaves itself by the displaceability of the outer body relative to Inner body the direction in which the radial sealing force works, specify exactly, because on the other hand the inner body sits non-rotatably on the eccentric pin and thus relative to Eccentricity can be precisely aligned.

With regard to the action of the outer body of the sealing force generating unit on the orbiting compressor body No further statements have been made so far. So one sees advantageous embodiment that the outer body acts on the movable compressor body via a rotary bearing. This ensures that the entire sealing force unit rotated with the eccentric pin and others on the one hand the movable compressor body essentially orbiting movement, preferably determined by a so-called Oldham coupling.  

A particularly advantageous version of the inventions sealing force generating unit according to the invention provides that the Pressure difference between the pressure chambers the outer body right relative to the inner body radially to the axis and in the direction of Eccentricity of the eccentric is applied.

In the context of the previous explanation of the pressure force generation unit was not discussed in detail how the pressure chamber advantageously with that to the outlet side Pressure proportional pressure can be applied, esp especially when the sealing force generating unit is non-rotatable sits on the eccentric and rotates with it. So look an advantageous solution that a pressure line to the are under pressure proportional to the outlet pressure leads the pressure chamber through the eccentric, and preferably also through the shaft supporting the eccentric, which makes the possibility speed is opened, the pressure line via the shaft to provide the annular groove.

Within the scope of the exemplary embodiments of the solution according to the invention are no further details made like the axial sealing force that the compressors body acted against each other, is generated. So one sees advantageous embodiment that one of the ver seal body in the direction of the other with a medium beats, its pressure is proportional to the output side Pressure is.  

This is preferably done with the compressor body which orbiting movement, so that the possibility be stands, one of the compressor bodies stationary in a housing to arrange the compressor while the other compressor body orbits on the one hand and thus the axial sealing force as well as the radial sealing force by the inventive Sealing force generating unit experiences.

The axial sealing force can then be particularly expedient generate when over a rear face of the Ver seal body an axial pressure chamber is arranged in which is then proportional to the output pressure Pressure can be generated.

This axial pressure chamber can advantageously be thereby execute that they are telescopic in the axial direction displaceable sealing ring, which the movement of the Compressor body follows in the axial direction.

This sealing ring is preferably in the axial direction spring loaded to ensure a secure fit of the same to enable all axial positions.

A particularly advantageous solution provides that sealing force generation within the axial pressure chamber unit is arranged, making a particularly compact solution is created.  

The solutions according to the invention, in which the radial Sealing force and / or the axial sealing force in each case by means of a pressure proportional to the outlet pressure generated not only have the advantage - as already described in detail - a definable sealing force for Is available to relatively the compressor body to hold other sealing positions. Have these solutions especially the great advantage that should - For example, by over-compression in the Spiralver denser - an overpressure in this occur, the relative Mobility between the compressor bodies that required is the radial sealing force and / or the axial The ability to make sealing force effective that opens the seal between the two compressors can be deliberately picked up at short notice to the overpressure builds up compensate, with the solution according to the invention Compensation of such an overpressure is thus firmly established it can be laid down that the effective radial and / or axial Have the sealing forces set precisely, which is then a threshold in the event that in between the compressor body-formed chambers overpressure arises.

The suitability of the invention described above Solution for pressure ratios from 5 to 20 in particular further improved by the fact that at least one inner end a spiral rib is thickened because this solution  opens up the possibility of compressing the final volume exactly defined and thus also the output pressure exactly, without the spiral ribs to the beginning of the Circular involvement to have to perform what produk technical problems with regard to the to be manufactured Would raise shapes. Due to the inner thickened end min at least one of the spiral ribs opens up the possibility the involute shape near the end due to the thickened shape leave.

Such thickened ends can be of various types and manner, for example, in the US A-4,781,549 a way of forming such thickened End described, other types of training such thickened ends can be found in US-A-3,802,809, EP-A- 0 122 722, US-A-4,547,137 and US-A-4,558,997.

Both spiral ribs are preferably thickened formed inner end, in particular the thickened Ends have identical shapes.

A particularly preferred variant of the invention The solution provides for the spiral ribs to be designed in this way are that there are two in the area of the thickened ends on the entrance side between the spiral ribs forming chamber unite a chamber, which between the ends up to a residual volume is reduced. This invention  Solution has the great advantage that unlike some solutions known from the prior art by the ver Thick ends are not aimed at that between these ultimately formed a chamber up to a volume is reduced, which theoretically corresponds to a zero volume, but deliberately a residual volume despite the thickened ends between these, which is the smallest volu men corresponds to the chamber, which is still sealed to each other adjacent spiral ribs of the two compressor bodies ent stands just before the ends of the spiral ribs other take off and the two following chambers with of the chamber reduced to the residual volume to combine at the further orbiting movement the common volume again reduce to the remaining volume.

This solution has the great advantage of having leaks avoids between the compressor bodies, which ent stand that in the last compression cycle in one overpressure occurs between the ends of the chamber, which leads to the fact that the compressor body relative to each other move others while sealing everyone between the Spiral ribs formed chambers is reduced. One of the like overpressure must not only be done by the fact that this occurs in the medium to be compressed, it can take place that in the medium to be compressed liquid or Oil is conveyed, which is aimed at a volume Zero between the thickened ends not fast enough that  means not as fast as the one to be compacted, preferably gaseous medium, can be displaced and thus the Er range of the theoretically zero volume counteracts that the thickened ends do not quickly can move enough towards each other. In this case occurs then just the reduction of Ab described above seal between all formed between the spiral ribs Chambers on.

A particularly advantageous solution provides that the Residual volume is at least across a cross section of an off extends opening, and thus in particular also serves displaced gas a sufficient cross-section still for Ver in order to reach the outlet opening.

A particularly preferred embodiment of the inventions Solution according to the invention provides that the outlet opening except half over from the end of the orbiting spiral rib painted area of the bottom surface of the stationary ver the body of the poet. This solution according to the invention has the great advantage that with this arrangement of the outlet opening of the previously known working principles of spiral compression ters can be deviated insofar as an outflow of the compressed medium, especially the compressed gas mediums, no longer from the position of the end of the orbi ting spiral rib is dependent and thus be conditional path control of the outlet of the to be compressed  Medium due to the orbiting movement is eliminated. So that can the outlet cross-section of compressed medium is completely independent controlled by the orbiting motion.

This solution thus opens up the possibility of the outlet conditions for the compressed medium completely independent of the orbiting movement.

The object of the invention is alternative or supplementary to the solutions described above for a compressor of the type described at the outset also according to the invention solved that one of the compressor body with a spiral rib an outlet channel located in the region of the inner end points, in which an lying in a wall of the end opening opens. This solution according to the invention has the great advantage that it is a completely new type of outlet the compressed medium, in particular the compressed gas shaped medium, opened because of the arrangement of the Aus the opening in the wall of the end of the spiral rib becomes the Outlet opening from the bottom surface of one compressor body relocated away and the control of the off is thus omitted cross section and also of the outlet as a whole through the orbiting movement. In addition, this to order of the outlet created the possibility to ver sealing medium under optimal spatial conditions, ins especially at high heights of the spiral ribs, emerge too leave, because the medium to be compressed does not have to be at the outlet  maximum over the entire height of the spiral ribs to the in a bottom surface of a compressor body flow opening, but it can be easily the maximum distance the compressed medium has to travel, reduced to a fraction of the maximum height of the spiral rib adorn.

This also opens up the possibility of the isentropic Ge overall efficiency of a compressor according to the invention better, because it also seals between the chambers canceling repercussions of the condensed medium avoided during final compression, the esp occur especially in all the solutions in which one chamber forming between the ends on one on one Compress volume insignificantly above zero be carried out because with such a small volume the last no compressed medium flowing out of the chamber has a sufficiently large cross-section available.

It is particularly advantageous if the in the outlet channel opening opening seen in the direction of the axis in is arranged in a central area of the wall, because with it is achieved that the maximum path that the condensed Medium to cover in the event of an outflow, at most half Height of the spiral rib or half the extent of the spiral rib in the direction of the axis.  

Regarding the type of in the end of the spiral rib preferred Exhaust duct have been associated with the previously solutions described no further details. So is it is particularly advantageous if the outlet channel through a Cavity is formed in the end of the spiral rib, wherein this cavity preferably has a flow cross section for Which is larger than that through the outlet opening provided flow cross-section is so that the compressed medium is only the outlet opening as the flow-preventing element must flow through, but then again the largest possible flow cross section which finds the outflow of the compressed medium the chamber formed between the ends not be prevents.

It is also particularly useful if the outlet opening having a spiral rib around the outlet opening giving guide pocket is provided. The guide bag serves in particular to flow to the outlet opening compressing medium with the least possible deflection and to lead to the outlet opening with as little turbulence as possible. About that in addition, the guide bag creates the possibility in a simple manner ability, a residual volume between the ends of the spiral ribs to provide so that the be The advantages described can also be achieved.  

A particularly useful solution provides that the Füh tion pocket is arranged at the end of the spiral rib, that in an end position of the orbiting movement the Spiral rib of the other compressor body with its end on both sides of the guide pocket in linear areas fits tightly. This solution ensures that the guide pocket forms at least part of the remaining volume and thus exactly in the end position of the orbiting movement, in which is the highest compression of the medium to be compressed is reached, with their full cross-section available stands to lead the compressed medium to the outlet opening.

Another solution in which is particularly advantageous each of the ends has a guide pocket and this in the End position are arranged opposite each other.

Another embodiment of an inventive Solution, in particular a training of the solution, in which the orifice outside of the end of the orbit the spiral rib swept area of the bottom surface of the stationary compressor body, provides that the off outlet opening is assigned an outlet valve. As a result the possibility of the outflow of the compressed medium de to control finely.

This control could, for example, by means of a Control controlled valve take place, the control Define control times according to different parameters can.  

However, sees a particularly advantageous embodiment before that the exhaust valve is pressure controlled. This simple one Solution opens up the possibility of the discharge of the verdich made dependent on the pressure reached and thus the possibility to be completely independent of the orbiting movement when the desired pressure is reached to open the outlet and later to ver accordingly conclude.

A particularly immediate valve effect is then achieved bar when the exhaust valve closes the exhaust port with a ven tilkörper overlaps, and thus directly the outlet opening assigned. This requires it in the case of one in the wall of the thickened end arranged outlet opening the outlet arrange valve so that this at least with the off valve body spanning the opening into the outlet channel or protrudes the cavity in the end.

If such a pressure-controlled exhaust valve is provided it is also necessary to use an anchoring element Valve. There is a possibility of this Veran Kerungselement of the valve in the outlet channel in the end of Arrange spiral rib. In this case it is advantageous the entire exhaust valve in the cavity of the end of the Spiral rib arranged.  

However, to be particularly advantageous for maintenance and assembly Creating relationships provides an alternative solution that the anchoring element of the exhaust valve outside of Outlet channel is arranged in the end of the spiral rib and at for example, over a rear face of the off the compressor compressor body.

Further features and advantages of the solution according to the invention are the subject of the following description and the graphical representation of some embodiments.

The drawing shows:

Fig. 1 shows a longitudinal section through a erfindungsge MAESSEN scroll compressor;

Fig. 2 is a fragmentary enlarged view of the area in Figure 1 to the sealing force generating unit;

Fig. 3 is a section along line 3-3 in Fig. 1;

Fig. 4 is a section along line 4-4 in Fig. 1;

Fig. 5 is a section along line 5-5 in Fig. 1;

Figure 6 is a fragmentary enlarged view of a first embodiment of ver thick ends of spiral ribs.

Figure 7 is a fragmentary enlarged view of a second embodiment of ver thick ends of the spiral ribs.

Fig. 8 is a fragmentary enlarged view of a third embodiment of ver thick ends of the spiral ribs and

Fig. 9 shows a section along line 9-9 in Fig. 8.

An embodiment of a compressor according to the invention, in particular a refrigerant compressor for normal and deep-freezing, preferably operating at pressure ratios of approximately 5 to approximately 20, shown in FIG. 1, comprises a housing, designated as a whole by 10 , in which a drive motor 12 is mounted.

The drive motor 12 comprises a stator 14 and a rotatable about an axis 16 rotor 18 , which is rotatably supported on both sides of the stator 14 by means of bearings 20 and 22 in each case in an interior of the housing 10 arranged end shield 24 or 26 .

On a side of the bearing 22 facing away from the stator 14 , an eccentric gear designated as a whole with 30 is arranged, which comprises an eccentric pin 34 arranged eccentrically with respect to the axis 16 on a shaft 32 of the rotor 18 , which in turn is designed as an eccentric bearing 36 as a sealing force generating unit engages, which in turn acts via an eccentric bearing receptacle 38 on a orbitally movable relative to a stationary compressor body 40 compressor body 42 . The stationary compressor body 40 is fixedly arranged in the housing 10 and extends over an entire cross section thereof transverse to the axis 16 . Between the stationary compressor body 40 and a front housing cover 44 there is an output pressure chamber 46 in which the medium to be compressed is present with the output pressure.

The outlet pressure chamber 46 is connected to an outer area of the stationary compressor body 40 through the longitudinal channel 48 in connection with a motor chamber 40 accommodating the drive motor 12 , the motor chamber 40 also being under outlet pressure.

It is preferably provided that when the housing 10 is arranged with the axis 16 lying, an oil sump 52 of lubricating oil is formed therein, the longitudinal channel 48 likewise being located in the oil sump 52 .

From the oil sump 52 , an oil channel 54 leads to the bearing 22 in the bearing plate 26 and opens there into an annular channel 56 surrounding a supported section 58 of the shaft 32 , so that the lubricating oil passes from the annular channel 56 into an annular channel 62 in the section 58 of the shaft 32 can.

From this ring channel 62 a radially to the axis 16 duri fender branch duct 64 leads into an interior of the shaft 32, is there to a for eccentric pin 34 towards extending longitudinal channel 66 through, from which in turn the eccentric pin 34 a ra dialer pass channel 68 to an outlet opening 70 in an outer peripheral surface 72 of the eccentric pin 34 leads.

As shown in FIGS. 2 and 3, the eccentric bearing 36 designed as a sealing force generating unit comprises an inner body 80 which is provided with a receptacle 82 for the eccentric pin 34 designed as a mating surface for the outer circumferential surface 72 of the eccentric pin 34 . The inner body 80 is fixed in a rotationally fixed manner on the eccentric pin 34 by means of a wedge 84 .

With the inner body 80 , two pistons 86 and 88 are firmly connected, preferably integrally formed thereon, wherein in the piston 86 a flush with the puncture channel 68 and in this through the mouth opening 70 also continuing puncture channel 90 is provided, which in turn has a mouth opening 92 ends in a piston crown 94 .

Both pistons 86 and 88 are each in a cylinder chamber 96 and 98 , both of which are arranged in an outer part 100 of the eccentric bearing 36 . Thus, the piston 86 in the cylinder chamber 96 delimits a pressure chamber 102 while the piston 88 in the cylinder chamber 98 delimits a pressure chamber 104 , the outer part 100 being displaced according to the pressure difference in the pressure chambers 102 and 104 relative to the inner part 80 .

Preferably, also the inner part 80 extending about parallel to a moving direction 106 of the pistons 86 and 88, guide surfaces 108 and 110 surfaces at corresponding guide 112 and 114 guided in the outer part 100, wherein the guide surfaces are ordered 108 and 110 on both sides of the receptacle 82 at.

Leads from the pressure chamber 102 as shown in FIG. 2, an axial pressure duct 108 into an annular chamber 110 from which starting in the region of the pressure chamber 104, a throttle passage 112 leads to the pressure space 104. Furthermore, from the pressure chamber 104, a pressure equalization channel 114 leads into a low-pressure chamber 116 located on the end face of the eccentric bearing 36 , which in turn is connected to a low-pressure channel 118 which runs transversely to the axis 16 through the compressor body 42 and is connected, for example, via axial embroidery channels 120 to one radially outer suction side of the two compressor bodies 40 , 42, which is under inlet pressure, is connected.

From the oil sump 52 is now pressed through the oil channel 34 lubricating oil via the ring channels 56 and 62 , the channels 64 , 66 and 68 and the channel 90 oil under outlet pressure in the pressure chamber 102 , so that there is also outlet pressure in this. Further, the oil, the possibility of entering via the axial passage 108, the annular passage 110 and the throttle channel 112 in the pressure chamber 104, wherein the throttle channel 112, a pressure reduction, for example to a low pressure level which is slightly higher than the inlet pressure, but nennens value below the output pressure lies, so that the oil from the pressure chamber 104 via the pressure compensation channel 114 , the low pressure chamber 116 , the low pressure channel 118 and the branch channel 120 is injected between the compressor body on the input side for lubrication.

At the same time, due to the pressure difference between the pressure chamber 102 and the pressure chamber 104, a force is exerted on the outer part 100 such that it moves away from the piston 86 in the direction 106 .

The piston 86 is arranged in such a way that the direction 106 corresponds to the direction of the eccentricity of the eccentric pin 34 relative to the shaft 32 , so that the outer part 100 , which is rotated together with the inner part 80 by the eccentric pin 34 , always with an in Direction 106 of the eccentricity force acting on the eccentric bearing 38 acts.

In order to allow rotation of the outer part 100 together with the inner part 80 and the eccentric pin 34 relative to the eccentric bearing 38 , the outer part 100 is surrounded by a bearing ring 122 which allows the eccentric bearing 36 to rotate in the eccentric bearing receptacle 38 about an eccentric axis 124 .

The eccentric axis 124 moves on a circular arc around the axis 16 , so that the eccentric bearing receptacle 38 carrying orbiting compressor body 42 moves orbiting around the axis 16 according to this circular path, the compressor body 42 being rotatable relative to one another by means of an orbiting movement allowing Oldham coupling 126 is guided to the stationary compressor body 40 .

Furthermore, the orbiting compressor body 42 is movable in the direction of the axis 16 and is therefore subjected to an axial force in the direction of the stationary compressor body 40 . This force is achieved by applying an outlet pressure to an inner region 130 which comprises the eccentric bearing receptacle 38 with the eccentric bearing 36 . This inner loading area 130 is separated from an outer area 132 by an axial ring seal 134 which has a sealing ring 136 which can be displaced in the direction of the axis 16 and which is acted upon by a spring assembly 138 in the direction of a rear end face 140 of the orbiting compressor body 42 and also a Front bearing plate 26 integrally formed on the guide ring 156 in a sealing manner in the radial direction, the guide ring 146 simultaneously serving to guide the sealing ring 136 in the axial direction. Before preferably, the sealing ring 136 is also provided with a radially narrower bearing ring 144 , which in turn rests on the rear end face 140 of the orbiting compressor body 42 .

The spring assembly 138 is preferably guided by the guide ring 146 and is supported on a flange surface 146 of the front bearing plate 26 .

The front bearing plate carrying the guide ring 136 forms an axial pressure chamber 148 which lies above the inner region 130 and which is connected to the motor chamber 40 on account of a connecting channel 149 , so that the starting pressure is present in this.

The outer area 132 of the orbiting compressor body 42 lying outside of the sealing ring 136 lies in an inlet pressure chamber 150 , which is also formed by the front end plate and into which an inlet nozzle 152 opens. The input pressure chamber 150 is also in communication with an outer side of the compressor body 40 and 42nd

The two compressor bodies 40 and 42 are each provided with a spiral rib 160 and 162 , which rise above a bottom surface 164 and 166 of the respective compressor body 40 and 42 and each have an outer wall surface 168 a and 170 a and an inner one Wall surface 168 b and 170 b have, which rise from the respective floor surfaces 164 and 166 , which are perpendicular to the axis 16 , parallel to the direction of the axis 16 over a height of preferably more than 30 mm and also run along a circular involute , which lies in a plane parallel to the bottom surface 164 or 166 .

The spiral ribs 160 and 162 are by the orbital movement of the movable compressor body 42 relative to the stationary compressor body 40 with their rib wall surfaces 168 a and 168 b or 170 a and 170 b against each other, with crescent-shaped chambers 172 and 174 forming between them , in which the medium to be compressed is conveyed from a radially outer inlet area 176 to a radially inner outlet area 178 and is thereby compressed.

These chambers 172 and 174 merge into a single chamber 179 before reaching the outlet area 178 .

Such scroll compressors are detailed, for example, in the article "Scroll Compressor Design and Application Characteristics for air conditioning ", heat pump and Refrigeration Applications, by J.P. Elson, G.F. Hundi and K.J. Moniet, published in Proceedings of the Institute of Refrigeration, Session 1990-1991, page 2-1 to 2-10 or U.S. Patent 4,781,549, to which full reference is made.  

The spirally formed ribs 160 and 162 are, as shown in Fig. 5 and Fig. 6, provided with thickened radially inner ends 180 , 182 , with which it is possible to compress the medium to be compressed as high as possible without the spiral Ribs 160 and 163 must be as close as possible to the base circle of the involute. The configuration of such thickened ends 180 and 182 is described, for example, in EP-A-0 122 722, US-A-4,547,137, and US Pat. No. 4,558,997 or US Pat. No. 4,781,549.

According to the invention, in the solution shown in FIG. 6, the thickened end 180 of the spiral rib 160 has an inner cavity 184 which, as shown in FIG. 1, thickened from an opening 188 in a rear end face 186 of the stationary compressor body 40 End 180 of the rib 160 extends and is preferably closed to the orbiting compressor body 42 .

In this cavity 184 opens an outlet opening 190 , which is arranged in a wall 192 of the thickened end 180 of the rib 160 facing the thickened end 182, specifically with respect to the extent of the wall 192 in the direction parallel to the axis 16 in an approximately central region, so that the outlet opening 190 is located in a plane parallel to axis 16 surface and enables the leakage of the compressed medium in the radial direction to the axis of the sixteenth

Furthermore, the wall 192 is provided with an inner contour facing the end 182 , which on the one hand, in an end position of the orbiting movement of the orbiting compressor body 42 shown in FIG. 6, relative to the stationary compressor body, in which the ends 180 and 182 just abut one another and still do not lift off, form two linear regions 194 and 196 , in which a wall 198 of the thickened end 182 faces the wall 192 , and also form a guide pocket 200 between these linear regions 194 and 196 , the inner contour 204 of which is linear relative to a connecting straight line 201 between these areas 194 and 196 is set back is extending into opposite the connecting line 201 in the wall 192 and passes over the area of its greatest distance from the connecting line 201 in the outlet opening 190th Furthermore, the guide pocket extends in the direction of the linear areas 194 and 196 beyond the outlet opening 190 and its inner contour 204 gradually approaches the connecting straight lines 201 with increasing proximity to the linear areas 194 and 196 .

Preferably, the inner contour 204 of the guide pocket 200 is arcuate in cross-section between the line-shaped loading areas 194 and 196 , the connecting straight line 201 forming a bowstring.

This guide pocket 200 serves, on the one hand, to guide the approaching ends 180 and 182 of the compressed medium present between the walls 192 and 198 as directly and as shortly as possible to the outlet opening 190 and, on the other hand, to ensure that in the end position described above the ends 180 and 182 relative to each other a noticeably large space for receiving displaced oil or displaced liquefied medium is available and in this end position between the ends 180 and 182 there is just no zero residual volume, as is the case in the US-A -4,781,549 is aimed for.

Preferably, the inner contour 204 of the guide pocket 200 is also recessed in the shape of an arc in cross-section in the direction of the axis 16 , so that it has a deepest-lying region 206 into which the outlet opening 190 opens.

In the first exemplary embodiment shown in FIG. 6, the wall 198 of the thickened end 192 has an inner contour 208 which extends essentially between the linear abutments 194 and 196 in the end position and which essentially approximates the connecting straight line 201 .

An even more advantageous embodiment of the solution according to the invention, shown in FIG. 7, in contrast to the solution shown in FIG. 6, also has a guide pocket 202 in the wall 198 , which in the described end position of the ends 180 and 182 of the guide pocket 200 is exactly opposite lies and is also formed with its inner contour 208 'arcuate with respect to the connecting straight line 201 .

Through these two opposing guide pockets 200 and 202 it is achieved that these in the end position of the orbiting movement in the area opposite the outlet opening 190 provide a sufficiently large gas flow cross-section for the outflowing gas, in order for this gas to flow as optimally as possible to the outlet opening 190 to lead and also form a significant space for receiving displaced oil or displaced liquefied medium, the largest accumulation of ver displaced oil or liquefied medium is formed near the outlet opening 190 .

As shown in both Fig. 6 and Fig. 7, the outlet opening 190 is seen ver with a pressure-controlled outlet valve 210 , which in the illustrated embodiment has a front flexible area 211 provided with lamella 212 , the opening movement of which is limited by a catcher 214 . The lamella 212 and catcher 214 are anchored, for example, with an anchoring element 216 , for example a screw, in the wall 192 , preferably in a thickened region 218 opposite the guide pocket 200 with respect to the linear region 194 .

The lamella 212 in turn lies against a wall surface 220 of the cavity 184 in the region of the wall 192 , the front region 211 of the lamella 212 engaging over the outlet opening 190 in the region of its confluence with the cavity 184 .

Alternatively, it is possible to replace the lamella valve another pressure controllable valve, for example a To provide a plate valve.

In a third embodiment, shown in Fig. 8 and 9, the lamella valve 210 'is arranged so that the lamella 212 with its front region 211 also from the outlet opening 190 in the cavity 184 abuts the wall surface 220 . The lamella 212 , however, extends, as shown in Fig. 9, starting from its front region 211 in the direction of the rear end face 186 of the compressor body 40 and from the opening 188 out u the anchoring element 216 , which is at a rear over the forehead area 186 uplifting projection 222 engages so that the Ver anchoring element 216 is freely accessible over the rear side 186 , whereby an assembly of the lamellar valve 210 'is easier tert. In the same manner as the fins 212, the catcher 214 extends so that blade 212 and catcher 214 only with their front portions extend through the aperture 188 into the cavity 184 and are thus easy to assemble.

Claims (27)

1. Compressor comprising a scroll compressor with a first compressor body and a second compressor body, the spiral ribs of which are designed in the form of a circular involute and which can be moved relative to one another in an orbital motion about an axis, with a medium to be compressed being sucked in on the inlet side, in between the compressor bodies Chambers are successively compressed and on the output side, a drive motor and an eccentric driven by the drive motor for generating the orbital movement of one of the compressor bodies, a radial and an axial sealing force acting between the compressor bodies, characterized in that between the eccentric ( 34 ) and the orbiting compactor body ( 42 ) is provided with a sealing force generating unit ( 36 ) generating radial sealing force to the axis ( 16 ), in the pressure chamber ( 102 ) of which a pressure medium acts which acts under pressure on the outlet side of the ver sealing medium proportional pressure is available. 2. Compressor according to claim 1, characterized in that the sealing force generating unit ( 36 ) rotates with the eccentric ( 34 ) and the axis ( 16 ). 3. Compressor according to claim 1 or 2, characterized in that the sealing force generating unit ( 36 ) as a double cylinder with two counteracting pressure spaces ( 102 , 104 ) is formed and that in one of the pressure spaces ( 102 , 104 ) proportional to the output pressure Pressure acts and in the other a reference pressure. 4. Compressor according to claim 3, characterized in that that the reference pressure is on the output side pressure is proportional pressure. 5. Compressor according to one of the preceding claims, characterized in that the sealing force generating unit ( 36 ) has an inner body ( 80 ) and an outer body ( 100 ) which are displaceable relative to one another in one direction and that one of them rotatably on the eccentric pin ( 34 ) sits. 6. A compressor according to claim 5, characterized in that the outer body ( 100 ) acts on the movable compressor body ( 42 ) via a rotary bearing ( 122 ). 7. A compressor according to claim 5 or 6, characterized in that due to the pressure difference between the pressure spaces ( 102 , 104 ) of the outer body ( 100 ) relative to the inner body ( 80 ) radially to the axis ( 16 ) and in the direction of the eccentricity of the eccentric ( 34 ) with the radial sealing force. 8. Compressor according to one of the preceding claims, characterized in that a pressure line ( 64 , 66 , 68 ) leads to the pressure chamber ( 102 ) standing under the outlet-side pressure proportional pressure ( 102 ) through the eccentric ( 34 ). 9. Compressor according to one of the preceding claims, characterized in that one of the compressor bodies ( 42 ) is acted upon axially in the direction of the other ( 40 ) with a medium whose pressure is proportional to the pressure on the outlet side. 10. Compressor according to claim 9, characterized in that an axial pressure chamber ( 148 ) is arranged over a rear end face ( 140 ) of the sealing body ( 42 ). 11. A compressor according to claim 10, characterized in that the axial pressure chamber ( 148 ) has a sealing ring ( 136 ) which is telescopically displaceable in the axial direction. 12. A compressor according to claim 11, characterized in that the sealing ring ( 136 ) strikes Federbeauf in the axial direction. 13. Compressor according to one of claims 10 to 12, characterized in that the sealing force generating unit ( 36 ) is arranged within the axial pressure chamber ( 148 ). 14. Compressor according to one of the preceding claims, characterized in that an inner end ( 180 , 182 ) at least one of the spiral ribs ( 160 , 162 ) are formed thickened. 15. A compressor according to claim 14, characterized in that the spiral ribs ( 160 , 162 ) are designed such that in the region of the ends ( 180 , 182 ) the two are formed on the inlet side between the spiral ribs ( 160 , 162 ) the chambers ( 172 , 174 ) combine to form a chamber ( 179 ), which is reduced between the ends ( 180 , 182 ) to a residual volume ( 200 , 202 ). 16. A compressor according to claim 15, characterized in that the residual volume ( 200 , 202 ) extends at least over a cross section of an outlet opening ( 190 ). 17. Compressor according to one of the preceding claims, characterized in that the outlet opening ( 190 ) lies outside half of a region of the bottom surface ( 164 ) of the stationary compressor body ( 40 ) which is swept by the end ( 182 ) of the orbiting spiral rib ( 162 ). 18. Compressor according to the preamble of claim 1 or according to one of the preceding claims, characterized in that one of the compressor elements ( 40 , 42 ) has a spiral rib ( 160 , 162 ) with an outlet channel lying in the region of the inner end ( 180 , 182 ) ( 184 ), in which a in a wall ( 192 ) of the end ( 180 ) lying outlet opening ( 190 ) opens. 19. A compressor according to claim 18, characterized in that the outlet opening ( 190 ) opening into the outlet channel ( 184 ) is arranged in the direction of the axis ( 16 ) in a central region of the wall ( 192 ). 20. A compressor according to claim 18 or 19 characterized in that the outlet channel is formed by a cavity ( 184 ) in the end ( 180 ) of the spiral rib ( 160 ). 21. Compressor according to one of claims 18 to 20, characterized in that a guide pocket ( 200 ) surrounding the outlet opening ( 190 ) is provided in the spiral rib ( 160 ) pointing to the outlet opening ( 190 ). 22. Compressor according to one of claims 18 to 21, characterized in that the guide pocket ( 200 ) is arranged at the end ( 180 ) of the spiral rib ( 160 ) that in an end position of the orbiting movement, the spiral rib ( 162 ) of the other Compressor body ( 42 ) with its end ( 182 ) lies on both sides of the guide pocket ( 200 ) in a linear manner ( 194 , 196 ) in a sealing manner. 23. Compressor according to one of the preceding claims, characterized in that the outlet opening ( 190 ) is associated with an outlet valve ( 210 ). 24. A compressor according to claim 23, characterized in that the outlet valve ( 210 ) is pressure controlled. 25. A compressor according to claim 24, characterized in that the outlet valve ( 210 ) overlaps the outlet opening ( 190 ) with a valve body ( 212 ). 26. A compressor according to claim 25, characterized in that an anchoring element ( 216 ) of the valve ( 210 ) in the outlet channel ( 184 ) in the end ( 180 ) of the spiral rib ( 160 ) is arranged. 27. A compressor according to claim 25, characterized in that the anchoring element ( 218 ) is arranged outside the outlet channel ( 184 ).