A SCREW COMPRESSOR WITH ADJUSTMENT SLIDE MEANS

Abstract: A screw compressor having an adjustment slide equipment for adjusting discharge pressure and capacity, respectively, is designed in an advantageous manner in that there is used a "large slide" (24), which is longer than the compressor screws (4, 6) and thereby, via a pointed end portion (14) and in connection with an axial displacement, is operable to effect pressure adjustment at the discharge port (10) without affecting the conditions at the intake end; at the latter, a capacity adjustment can be effected by means of an auxiliary slide (26) which, seen in cross section, forms part of the large slide, and which is separately axially displaceable in a groove (30) therein, such that it is possible to open this groove to a variable degree towards the meeting area of the screw rotors. This basic design in connection with an unusually large diameter of the main slide (24) provides for several advantageous possibilities discussed in greater detail.

Description: A SCREW COMPRESSOR WITH ADJUSTMENT SLIDE MEANS. The present invention relates to a screw compressor having slide means for adjustment of capacity and compression, respectively. The capacity is adjusted at the intake end in that the slide means are caused to change the axial location of the area, from which the two co-operating screw rotors "cut off" the intake gas, such that the cut off gas can only be housed inside the remaining axial working length of the two rotors, while the degree of compression is determined by way of such a slide adjustment which affects the effective degree of opening of the discharge port of the compressor. The gas discharge takes place both radially and to a smaller degree axially, and it is thus possible to adjust it by a more or less pronounced projection of a wedge body into a fixed discharge port in the compressor housing at the discharge end of the screw rotors . In practice, the said slide means are arranged at the "meeting side" of the counter rotating screw rotors, with the discharge port located at the end of this area. The slide means should fit very closely to the surface configuration of the rotors, though out of touch therewith, whereby the slides comprise an elongated sealing part with a roof ridge like cross section and an associated guide body part mounted in a guiding groove in the wall of the compressor housing. In practice it is preferred to make use of a circular cylindrical shape of the said body part, even though this may seem unsuitable in view of the fact that the "roof ridge part" should be stabilised in the lateral direction in such a man- ner that with its extremely close proximity to the rotor surfaces it should be effectively prevented from being laterally displaced or rotated into touch with these surfaces. A cylindrical body part is not effective for this purpose, but for economical reasons it is necessary to use reasonably simple working techniques, also for the shaping of the guiding groove of the compressor housing. It should then in some other way be ensured that the slides as respective wholes cannot rotate in the part cylindrical guiding groove. The are known more different solutions of this problem, e.g. the use of a cut axial guiding track in the slides diametrically opposite to the active sealing part, whereby a fixed pin or roller of the compressor housing may intrude into this track and thus prevent a rotation of the slide. According to another known solution the 'roof ridge part 1 is anchored in the transverse direction in being in a direct, sliding guiding engagement with the side walls of the said discharge port and intake port, respectively. However, these guiding principles suffer from certain drawbacks, which should be seen in connection with the remainder of the slide construction, confer remarks below. If it was or is desirable to be able to effect an adjustment solely of the degree of compression, then this is achievable by means of a single slide, which can be axially displaced such that its pointed front end can fill out the discharge port to a higher or lesser degree, while at the intake port it will seal against the rotors irrespective of its axial position. The problem underlying the invention is that a natural desire of an adjustability even of the capacity of the screw compressor will require the effective length of the slide to be variable, such that at the intake area the slide can provide for a more or less pronounced rotor sealing or, respectively, a cancellation of such a sealing along a cer- tain axial length, whereby the rotors cannot build up neither a suction nor a compression effect along this length. Traditionally, this has resulted in the slide means being constituted by two coaxially arranged slides which, by suitable moving means, are axially displaceable in such a manner that the foremost slide is controllable to a graduated projection into the discharge port, while a rear slide is separately axially displaceable such that at the intake end it may define a more or less wide gap between the two slide elements for adjusting the intake capacity. The two slide ele- ments should be axially coupled together in a sort of telescopic system, and this is the reason for the above indicated problems to exist: In response to various external forces, e.g. originating already from thermal influences, the two slide elements may behave in an almost inpredictable manner, whereby the said telescopic connection may be subjected to uncontrolled and highly damaging flexing in view of the extreme tolerance requirements . On this background and in connection with the invention it has been realised that it is indeed possible to provide a slide, which can act as a unitary, stiff member, viz. in the form of a large-slide which, itself, has a length sufficiently for it to carry out a full adjustment displacement at the discharge port, without thereby being displaced so as to expose the rotors at their intake ends, said large slide over a length at the intake end being shaped with a guiding groove in the very 'roof ridge area' of the slide, in which groove there is slidably received a mini slide, which has a portion projecting from the groove so as to complete the large slide in forming the said roof ridge portion, said mini slide being axially guidable between an advanced position, in which it fills out the guiding groove, and a retracted position, in which the groove is open towards the rotors at least along a substantial partial length of the groove. In this manner it will be possible to still effect a capacity adjustment, even though the width of the minislide is noticeably smaller than the total width of the roof ridge area of the large slide; even a relatively narrow shorting between the rotors will give rise to such a drop of compression that this can be used directly for a capacity adjustment. The invention presents more different constructional and functional aspects. The reference to a large slide should not only apply to the slide length, which, in total, will be greater than the length of the rotors, but also to the cross sectional size of the slide, which should preferably be relatively large, viz. of the same magnitude as that of the ro- tors, while conventionally the slide size has been considerably smaller. According to the invention it is even a preferred feature that the guiding groove for the large slide is made with exactly the same diameter as the rotor bores of the compressor housing, as this will favour a rational working of the precast compressor housing. However, irrespectively of the more detailed design of the large slide there are circumstances worth being mentioned on the background already discussed: 1) The large slide will have the character of a very stiff beam, this being unaffected by the presence of the minislide. The large slide is influenced crosswise by the compression pressure, with a maximum adjacent the discharge port. Inasfar as the pressure is countered at the area between the opposite ends of the slide, the latter as a whole will be forced against its guiding base in a well defined manner, such that there will be no remaining uncertainty with respect to force phenomena as in the known telescopic connec- tions. 2) Due to the fact that the 'roof ridge faces' of the large slide will engage with the rotors over an increased peripheral portion thereof, it is possible to design the discharge port with generally increased dimensions, this being highly advantageous in particular in connection with gasses of a low specific volume and at high suction pressures. It has previously been theoretically realised that the port areas used so far have been smaller than an optimal size, but it has been necessary to choose a compromise between ideal conditions at the intake port and the discharge port, respectively; this necessity, however, is eliminated by the present invention. 3) At the intake end it is correspondingly ideal that the large slide permanently forms a prolongation of the walls of the fixed rotor bores, only leaving space for the relatively narrow minislide adjacent to the very roof ridge area. In traditional systems with double slides, an opening of an axial gap between the slides implies a strong shorting between the rotors, and it is quite customary that a capacity adjust- ment over an almost full range between 100% and 10% is effected by a relative slide displacement of only some 1/8 of the length of the rotors. With the use of the minislide for this purpose the adjustment length can be increased noticea- bly, e.g. up towards the half of the rotor length, whereby it is possible to effect a fine adjustment, if so desired, much more effectively without in any way compromising the improved conditions at the discharge port. Thus, the use of the large slide/minislide concept of the invention is very advantageous, but there are some associated problems which, in principle, could be disregarded in the present connection, but which have also been settled by the development of the invention for practical use. A problem is that due to its large size the slide will be influenced by very high forces. Radial forces from the compressed gas act on the relatively large roof ridge faces, whereby the slide is forced very strongly against its opposite guiding face, but this is compensated for by virtue of that guiding face being correspondingly relatively large. The entire, large front end area of the slide will be located in the discharge zone of the compressed gas, whereby the slide is influenced by high retraction forces. Even with the use of a "big beam" slide, there may still occur arbitrary radial forces directed towards the rotor surfaces, and when the relevant spacing should be a matter of micrometers it will be important to provide a suitable support for the slide not only away from, but also towards the rotors. Moreover, the axial pressure should be countered or compensated for by correspondingly high counter forces in the system used for controlling the adjustment movement of the slide. These potential problems connected with the invention have been overcome partly by providing additional radial support means and partly by an axial force balancing of the large slide by using the pressure of the discharge gas. These special concepts, which could even be advantageously applicable in conventional systems, will be explained below in more detail, in connection with a description of the invention with reference to the drawings, in which: Fig. 1 is a longitudinal sectional view of a conventional screw compressor; Fig. 2 is a cross sectional view thereof; Figs. 3 and 4 are corresponding views of a screw compressor according to the invention; Figs . 5 and 6 are further corresponding views showing in greater detail a preferred embodiment of the invention; Fig. 7 is a longitudinal section seen from above along the line VII -VII of Fig. 6; and Figs. 8-12 are longitudinal sectional view of the compressor shown with its parts in different positions. In a conventional manner, the screw compressor shown in Figs. 1 and 2 has a compressor housing 2 with two screw rotors 4 and 6, the screw threads of which are sealingly inter- engaging and operate in the manner that they currently form thread chambers which are at first in open connection with an intake or suction conduit 8, whereafter they are closed and then narrowed for compression of the intake gas towards a more or less restricted discharge port 10 which, in a manner not shown, is connected to the pressure system to be served by the compressor, e.g. a refrigeration system. In alignment with the intake and discharge ports 8 and 10 and next to the meeting area of the rotors there is arranged a slide system comprising a foremost slide 12 with a front depression 14 and a rear slide 16. Both of these slides have the cross section shown in Fig. 2, and it will be noted that the slides seal operatively against the rotors by means of 'roof ridge faces' 18 meeting in a sharp ridge. In general, these faces are just a completion of the rotor bores of the compressor housing for complete covering of the rotor peripheries, but because they are axially displaceable these slides can be used for adjustment purposes. Thus, by a displacement of the slide 12 effected by means of a piston 20 in a protruding control cylinder 22 the front depression 14 may be projected more or less widely into the discharge port 10, whereby the degree of compression can be adjusted. The slide 16 can be correspondingly displaced by means of non- illustrated moving means, whereby a more or less wide gap 23 can be provided between the slides 12 and 16, invoking a more or less pronounced degree of operative, direct shorting between the rotors 4 and 6, whereby it is possible to adjust CO c t to P 1 P 1 LΠ o Π o LΠ o cπ Ω rt Hi 3 TJ Φ a' H PJ H H Φ 0 Hi Φ rt 3 CL CQ PJ CQ CQ P- rt ^ a a P- tr H Φ J Φ 3 Φ LQ Φ . 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Ω ra 0 < rt CL > < Hi PJ P- φ Φ a Φ PJ Hi a ra P- Φ 00 Hi ≤ rt CQ rt P- h-" P- Hj φ 0 tr ra a P- * cr φ CQ Φ P- rt PJ rt P- CQ Hi TJ rt 0 O tr tr a 0 CQ <! 0 < P, N a Hj PJ J a CL rt PJ a Ω Φ CL CL Φ TJ a Hi 3 Hj Φ φ TJ Ω 0 Φ < P- 0 rt Hj ra ra • rt rt φ Hi ra tr J Hi P- 0 P- CL 0 Hi PJ 0 PJ Hj ^ 1 3 tr Hi P- tsi rt PJ LQ φ "< rt 3 rt PJ 3 a Hi Hi Hi 0 rt ^ PJ Φ i Pi Ω CL . 0 rt a φ Ω CQ P- rt P- O Φ CQ Q φ Hi rt rt 0 cr Ω Hj rt Pi φ Hj tr ' 1 a ' a a Ω 0 PJ ^ Hj cr • PJ P- LQ tr 3 CL i ra Φ Φ CL rt Hi 1 Φ a 1 φ Φ rt auxiliary pressure at its front end. In this manner the slide may be axially balanced, such that for an operative displacement of the slide it is sufficient to apply small added forces, no matter how big the occurring pressure difference is . This cylinder/piston system may be arranged internally in the slide itself, while an associated control system can be arranged with short axial spacing from the slide or the slide housing, such that the said conventional piston/cylinder sys- tern 20,22 can be entirely avoided. It is important that the total building length of the compressor may hereby be reduced by avoiding the external control cylinder for the slide adjustment . Figs. 5-7 show an embodiment which is preferred in prac- tice and which makes use of a gear motor with an associated screw spindle for controlling the slide adjustment. The general layout with the slide 24 in Fig. 5 can be recognised from Fig. 3, including the cam roller groove 32. The slide is provided with an eccentrically located cylinder bore 36 which is sealingly inserted over a foremost, fixed cylinder part 38 projecting rearwardly from a flange 40 secured to the compressor housing. At the rear, the bore 38 is slidably sealed against a fixed, forwardly projecting cylinder 42 having near its middle a fixed cross wall 44. At its middle area, the slide 24 is provided with a cup cylinder 46 which, as shown in Fig. 5, can project over the cylinder 42, while for a movement of the slide towards the right it can slide forwardly inside the fixed cylinder part 38, without sealing thereagainst , as shown in Fig. 7. The cylinder space between the cup cylinder 46 and the front flange 40 is denoted 48. At the rearmost, closed end of the cam roller groove 32 there is provided a radial hole 50, which as shown in Fig. 7 is located at the rear end of the cup cylinder 46 and forms a connection to the open cylindrical space between this cylin- der and the fixed cylinder 42. Thus, the pressure from the discharge end of the compressor will be conveyed through the groove 32 and the hole 50 to the space, designated 52, between the front end of the cup cylinder 46 and the fixed mid- die wall 44, i.e. this pressure will seek to force the slide towards the right, while the same pressure at the front end of the slide seeks to force the slide to the left. Correspondingly, it is desirable to connect the space 48 to the suction pressure side of the compressor, such that the pressure in this space or chamber will be independent of the chamber being expanded and narrowed by the movements of the slide. Such a connection may be arranged externally, but it is preferred to arrange it internally in the following man- ner: As shown in Fig. 6, the slide 24 is provided with a pair of channels 54 and 56 which extend forwardly from the rear end of the slide, with a length almost the same as that of the guiding groove 30 for the minislide, and these channels are in flow connection with the groove 30 through a row of transverse holes 58. The channels 54 and 56 extend to the area adjacent the said radial hole 50, where they end at a block portion 60, shown at the bottom of Fig. 7, in front of which the internal diameter of the outer cylindrical body of the slide widens for co-operation with the fixed front cylinder 38. According to Figs. 6 and 7, a pair of through bores 62 are provided in the block portion 60 at the end of the channel 56, whereby the channel 56 will be in open flow connection with the said widened space, which, via the gap be- tween the cylindrical parts 38 and 46, will be correspondingly flow connected with the space 48. Thus, the latter space will be in permanent connection with the suction side of the compressor. As shown in Fig. 7, the fixed middle wall 44 carries an electric or hydraulic motor 64 which, via a tight transmission such as a magnet coupling, drives a gear 66 rotating a screw spindle 68. This spindle projects forwardly through a nut bushing 70 in the closed end of the cup cylinder 46 and further to a bearing 72 in the fixed front flange 40. Inasfar as the pressure differences acting on the large slide will be practically balanced out no matter the operational conditions, the slide position can be adjusted with the use of a relatively small motor 64, and the nut bushing co co to to P 1 cπ o LΠ o LΠ o cπ rt LQ s; CQ TJ Ω rt s- TJ a rt P- TJ P- CQ cr 0 rt 3 Ω tr Hj tr a P, p- tr HJ 0 tr • HJ a -> Hj Hh tr Φ h- 1 0 Φ P- Ω φ 0 0 Φ 0 rt φ Φ Φ LQ P- P- Φ a 0 a Φ Ω tr ra CQ a HJ ι_ι. Φ • ra CL φ rt HJ rt CQ LQ tr H ra Φ H Φ Φ CL Ω m 0 Φ H Hh a ^ tc Φ ra Φ tr a rt P- a cr Ω 0 Hh P- Hi a φ Φ 0 ι-3 rt tr 0 rt ^ rt rt 3 a 0 0 *< Hj Hi 0 rt a tr tr f τ] J a a" *j P- tr TJ a rt a ^i φ Hi tr o Φ Φ P- rt Φ P- a a i Hi • tr H-> P- CL Pi i Φ s; a LQ LQ 0 LQ rt φ ^ Φ < CQ Φ Hj Hi rt 3 Hh i L . ra H - CQ LQ rt tr 0 P- P- Pi P> a C a P- Φ LQ rt ra TJ tr CL Ω Φ φ Φ TJ a a 1 L CQ o X a tr 0 Hi Φ P- P- oo Hi Hj Φ P- ra o Ω rt P- φ Hi 0 ra CQ P- CQ ^ a PJ ra 0 rt tr rt p. 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P- a L Φ φ CL a Φ 0 CQ rt rt P- tr a- Φ rt 0 CQ CQ Ω Hi CL TJ CL Hi tr Φ tr CL 0 Φ P- P- TJ rt 0 o P- TJ PI a CL φ Φ : > O 0 rr rt Pi P- Hi Hi Hi a Pi Ω rt ra Hj ^ P- a Hi a CQ CQ Hi o ^ CQ PI tr Hi φ a 0 3 Φ PJ Hj rt P- TJ Φ a ≤ P- P- Hi LQ Hi rt 0 Ω PJ P- ra Ω Ξ tr a P Pi P- 1 P- • a Φ 3 tr a a CL 3 TJ tr J Φ LQ Ω LQ rt φ Pi CQ CL Pi Φ 0 CL Pi 0 P- Hj TJ P- Hi • ; tr • Hi TJ P- P- CQ P- P- a φ CL Ω P- rt 0 rt φ Hi PJ rt Φ a Φ a L < 0 0 CQ ^ 0 Ω €, φ Ω Hi Pi L ra CL rt rt P- P- ^ a a rt • <; P- Hj rt Φ CL t_ι. Φ TJ i a a Q rt 0 Φ O 3 rt P- HJ t_J. a Pi TJ Hi o P- CQ LQ ra P- Hi a P) CQ P- tr CL <! Φ a CQ ra 0 3 CQ a 0 rt 0 rt LO Φ a Φ Φ a CQ rt ra ra Φ P- φ ^ 3 a cr O CL P- 3 a rt rt 3 0 P- CL rt CL Pi PJ CL a 3 - 3 Pi 0 ^ 3 φ Ω rt P- P- TJ X ra P- 3 m P- TJ a X rt - TJ φ a P- P- J 0 HJ P- a φ a' : > 0 3 P- Φ 0 a rt Pi 0 rt a 0 3 rt Pi CL P- tr ra 3 Cb ra ra rt rt a Φ - ι_l. a o P- a Φ P- 0 i a tr P- 3 Φ Φ 3 a LQ Pi Hj rt H 3 rt o rt Hi o CL CL P- Ω s; CL 3 Φ P- tr a P- J < φ a rt Ω P- P- 0 ra cr o Ω 0 Φ 0 a φ 1 Φ 0 CL Hi a 0 ^ a 0 TJ CL a LQ 1 CL 3 φ Φ - 3 φ CQ Φ 1 Ω i cr 1 a cr ^ 1 Φ 1 Φ driving cylinder 28', such that there is still operated with 100% intake capacity. In Fig. 11 the slide 24 assumes the same middle position, but with the minislide 26 somewhat retracted, such that at the front end of the groove 30 there is formed a shorting space, in which no effective intake suction can be effected, and from which already sucked-in and partially compressed gas may escape to the intake end of the compressor as indicated by a dotted return arrow. Use is hereby made of the hole con- nections 58 (Fig. 6) between the guiding groove 30 (Fig. 4) of the minislide and the axial return channels 54 and 56 in the slide. In Fig. 12 the slide 24 is shown extremely projected, for maximum closure of the discharge port 10, while the minislide 26 is preferably entirely retracted so as to condition a minimum of capacity, i.e. in general with minimum load of the compressor. The slide 24 and its minislide groove 30 will here be projected to a position widely in front of the front end of the minislide 26, such that initially sucked-in gas, if any, can readily escape for returning to the suction side as indicated by arrows. Thus, the entire stretch forwardly to the rear end of the slide 24 will be an inoperative bypass stretch, in which the return holes 58 and channels 54,56 will be substantially inoperative. It should be mentioned that in connection with the invention it has been found desirable and realizable that the minislide 26 is not adjusted gradually between its extreme positions, but is controlled only for full opening or closing of the groove 30, this highly facilitating the control of this slide. Certain transient problems may occur, but these will be widely compensated for by virtue of the slide 24 being able to rapidly adjust itself in a stable manner for achieving a suitable compression effect.

Claims: C L A I M S : 1. A screw compressor with a compressor housing accommodating two parallel and interengaging screw rotors, which extend axially between an intake port and a discharge port at opposite ends of the compressor housing and cooperate with a system of slides, which are displaceable in the same axial direction and, generally, are sealing against a peripheral meeting area between the screw rotors, the slide system being shaped such that at the discharge port there is a wedge formed nose portion which, by a controlled axial displacement, is operable to block the discharge port to a higher or lesser degree for adjusting the resulting degree of compression, while at the intake end separately displaceable slide means are provided for adjusting the intake capacity of the compressor, chracterized in that the slide system is embodied partly as a single slide, which is longer than the screw rotors, such that when adjusted axially it can block the discharge port of the compressor housing to a higher or lesser degree, while at its rear and independently of such an ad- justment it can steadily fill out the cross section of the intake port of the compressor housing, and partly as an auxiliary slide which, at the intake end of said single slide is received in a guiding groove therein along an outer stretch of the meeting area between the screw rotors, where the aux- iliary slide completes the sealing cross section of the single slide against this area, said auxiliary slide being axially displaceable in said guiding groove and connected with separate control means for its displacement between a projected position, in which it fills out the guiding groove, and a retracted position, in which the guiding groove is open towards said meeting area over the full or a partial length of the guiding groove . 2. A screw compressor according to claim 1, characterized in that the single slide is made with a relatively large di- ameter, viz. of the same magnitude as the diameter of the screw rotors, and that it seals against these along partcyl- indrical segments wider than the corresponding sealing segments of the auxiliary slide. 3. A screw compressor according to claim 2, characterized in that the guiding passage of the compressor housing accom- modating the single slide is made with the same diameter as the rotor bores of the housing. 4. A screw compressor according to claim 1, characterized in that the single slide is stabilized in the cross plane by means of height adjustable side rollers (34) in engagement with longitudinal guiding grooves (32) in this slide. 5. A screw compressor according to claim 4, characterized in that the side rollers, which prevent the slide from getting in touch with to rotor surfaces, are provided adjacent to the discharge ends of the rotors. 6. A screw rotor according to claim 1, in which the front end of the single slide is subjected to the discharge pressure of the compressor, while its rear end is subjected to the suction pressure thereof, characterized in that the slide itself is designed as or with a cylinder/piston system fill- ing out approximately the half of the cross sectional area of the slide and is subjected to the discharge pressure at its rear end and to the intake pressure or an auxiliary pressure at its front end. 7. A screw compressor according to claim 6, characterized in that the discharge pressure is applied to the internal system through a side groove in the slide and a cross hole in the slide wall, said groove being open towards the discharge end. 8. A screw compressor according to claim 6, characterized in that the suction pressure is applied to the internal system through a channel directly through the rear end portion of the slide. 9. A screw compressor according to claim 1, characterized in that the guiding groove of the minislide, through side holes in the groove wall, is in flow connection with axial channels debouching freely in the intake chamber of the compressor. AMENDED CLAIMS [received by the International Bureau on 16 March 1998 (16.03.98); original claims 1-6 and 10 amended; remaining claims unchanged (3 pages)] 1. A screw compressor with a compressor housing accommodating two parallel and interengaging screw rotors, which extend axially between an intake end and a discharge port at opposite ends of the compressor housing and cooperate with a system of slides, which are displaceable in a guide passage in the same axial direction and, generally, are sealing against a peripheral meeting area between the screw rotors, the slide system comprising two radially interengaging and axially mutually slidable slides, one partially encircling the other, and of which one has a wedge formed front end portion which, by a controlled axial displacement, is operable to block the discharge port to a higher or lesser degree for adjusting the resulting degree of compression, while the other slide, in being separately axially adjustable, serves the purpose of enabling an adjustment of intake capacity of the compressor more or less adjacent to the intake end of the rotors, characterized in that the slide system is embodied partly by a predominant compression ratio adjusting main slide, which is longer than the rotors and generally fills out the entire cross section of said guide passage, and partly by a relatively narrow auxiliary slide which, at the intake end of said main slide, is received in a guiding groove therein along a rearmost stretch of the meeting area between the screw rotors, where the auxiliary slide completes the sealing cross section of the main slide against this area, said auxiliary slide being axially displaceable in said guiding groove and connected with separate control means for its displacement between a projected position, in which it fills out the guiding groove, and a retracted position, in which the guiding groove is open towards said meeting area over the full or a partial length of the guiding groove. 2. A screw compressor according to claim 1, characterized in that the main slide is made with a relatively large diame- ter, viz. of the same magnitude as the diameter of the screw rotors, and that it seals against these along partcylindrical segments wider than the corresponding sealing segments of the auxiliary slide. 3. A screw compressor according to claim 2, characterized in that the guiding passage of the compressor housing accom- modating the main slide is made with the same diameter as the rotor bores of the housing. 4. A screw compressor according to claim 1, characterized in that the main slide is stabilized in the cross plane by means of height adjustable side rollers (34) in engagement with longitudinal guiding grooves (32) in this slide. 5. A screw compressor according to claim 4, characterized in that the side rollers, which prevent the slide from getting in touch with the rotor surfaces, are provided adjacent to the discharge ends of the rotors. 6. A screw rotor according to claim 1, in which the front end of the main slide is subjected to the discharge pressure of the compressor, while its rear end is subjected to the suction pressure thereof, characterized in that the slide itself is designed as or with a cylinder/piston system filling out approximately the half of the cross sectional area of the slide and is subjected to the discharge pressure at its rear end and to the intake pressure or an auxiliary pressure at its front end. 7. A screw compressor according to claim 6, characterized in that the discharge pressure is applied to the internal system through a side groove in the slide and a cross hole in the slide wall, said groove being open towards the discharge end. 8. A screw compressor according to claim 6, characterized in that the suction pressure is applied to the internal system through a channel directly through the rear end portion of the slide. 9. A screw compressor according to claim 1, characterized in that the guiding groove of the minislide, through side holes in the groove wall, is in flow connection with axial channels debouching freely in the intake chamber of the compressor. 10. A screw compressor according to claim 6, characterized in that the main slide is controlled in its longitudinal direction by means of an internally provided moving system, preferably embodied as a gear motor co-operating with a screw spindle which, when rotated, operates to drive the slide in the longitudinal direction.

Inventors: SKOVLUND ANDERSEN LARS, SKOVLUND ANDERSEN, LARS
Applicants: SABROE REFRIGERATION A S, SKOVLUND ANDERSEN LARS, SABROE REFRIGERATION A/S, SKOVLUND ANDERSEN, LARS
Application year: 1997
Main classification: F04C29
IPC codes: F04C18, F04C28