EP0114298B1 - Heating chamber for running yarns - Google Patents

Description

The invention relates to a heating chamber for running threads. This heating chamber is suitable for the treatment of a thread with saturated water vapor (saturated steam) under increased pressure.

The particular problem with such heating chambers is that the saturated steam escapes through the thread inlet and outlet in such large quantities that the operation of the heating chamber is uneconomical.

To remedy this, labyrinth seals and gap seals at the thread inlet and thread outlet are already known. Labyrinth seals, which consist of plates stacked on top of each other with diaphragm openings, which form a wide opening due to the relative movement of the plates in the threading position and a labyrinth in the operating position (DE-A-2643787, US-A-2,529,563, US-A-2,351,110) suitable for threading, but have proven to be fundamentally unsuitable in operation, since the need for undisturbed thread running cannot be reconciled with the need to provide a tortuous outlet path to avoid loss of heating medium. Gap seals are indeed suitable. With them, a large gap length results in a sufficiently large reduction in losses. However, as the gap length and the gap width increase, threading, in particular pneumatic threading, becomes an insurmountable problem. From DE-A-2703991 and 2855640 heating chambers for saturated steam are known, in which the sealing of the heating chamber in the end regions is carried out by bolts with a groove running along the surface line, which bolts are inserted axially into a bushing in a sealing manner. In the known heating chamber, threading is readily possible by removing the bolts from the end regions, but when the bolts are inserted, the thread is easily damaged, since the thread does not run at a defined point, and it is a very significant disadvantage that When threading the thread, cool the bolts to such an extent that a steady operating state can only be reached after threading in after a long time and with a correspondingly high thread drop. In addition, the known heating chamber is complex in terms of production technology and poor in terms of operation.

According to this invention, several properties of the heating chamber serve alone or in combination for rapid heating after a steady and steep temperature curve over time and operation without temperature fluctuations. This measure above all prevents local accumulation of condensate. The theory could be established through experiments that any local condensate formation, e.g. in the form of drops, noticeable during the heating and operation of the heating chamber by significant temperature jumps.

The present invention solves these disadvantages of the prior art and the problems presented in that the two bodies that make up the heating chamber at least in the end regions lie on one another with their flat or curved surfaces (closing surfaces) and slide relative to one another on these surfaces and are movable transversely to the surface distortion (surface deformation) introduced in at least one of the closing surfaces. The closing surfaces are adapted to one another in such a way that the pressure medium, i.e. the saturated water vapor does not escape even at high pressure. The thread channel serving for thread guidance is formed in that the surface of the first body perpendicular or transverse to the direction of movement has at least one recess in the form of a groove, step or similar warp (surface deformation) which extends along the thread path and is straight or curved. This surface deformation is covered in the one relative position of the two bodies (operating position) by the closing surfaces of the second body, so that a narrow thread guiding gap (thread channel) is created in this relative position, which is narrow enough to avoid impermissible pressure losses of the heating chamber, and which is shaped in this way is that there is a targeted pressure reduction along the gap with targeted cooling of the thread.

If the surface deformation in the first body is a thread-guiding groove, which in one relative position is covered by the closing surface of the other body, the closing surface of the second body in one embodiment of the invention also has a groove (threading groove), the other Relative position (threading position) of the two bodies covers the thread-guiding groove of the first body and forms with it a wide gap suitable for the axial threading of the thread, in particular the pneumatic threading. This only the threading groove of the second body (threading groove) is preferably larger in cross section than the thread groove of the first body and has bevelled flanks at least on one side, on which the thread when the body is retracted into the relative position in the direction of the thread groove of the first body is distracted.

In another embodiment of the invention, the surface deformation of the closing surface of the second body is carried out as an end edge of the closing surface or slot in the closing surface of the second body, which in the threading position of the body releases the thread groove in an insertion plane and thereby the insertion of a running thread transverse to it Running direction allowed. The surfaces can be flat or curved in the thread running direction and / or slightly curved transversely to the thread running direction.

If the body as a flat or curved plat ten, the closing surfaces of a body can also lie in two planes that intersect in the area of the surface deformation, so that the surface deformations form steps of equal size in both bodies. In this version, the steps in the operating position of the two bodies form a narrow gap and, depending on the size of the relative movement in the threading position, either an extended gap suitable for axial threading or a thread insertion slot for inserting the running thread if the step of one's own body is the front edge of the dominated other body in the threading position.

The thread heating chamber according to the invention can be in the operating position of the two bodies, in particular at the thread entrance and / or thread exit, to a small width of the thread channel of e.g. 0.2 to 0.5 mm width can be set so that a running thread can be guided undisturbed, but the losses of the heating medium are low. The gap width, in particular in the thread outlet area, can be different over the gap length. Relaxation chambers or vacuum chambers can also be connected to the gap in order to obtain a targeted pressure relaxation gradient along the course of the thread.

In one embodiment of the invention, the heating chamber according to the invention can have, for sealing in the end regions only, the bodies which are movable towards one another with surface deformations, one of the bodies being fixed in place on an end flange of the heating chamber and the other being able to perform a relative movement. In this embodiment, the bodies are preferably designed as inner cylinders and outer cylinders which can be rotated relative to one another. Because an axial movement is forced on one body at the same time, it can be achieved that this body lies sealingly against the end flange. For this purpose, the bodies are preferably provided with a thread pairing, the groove of the inner cylinder being cut down to the thread base. In this version, the thread forms a labyrinth with an additional sealing effect in the operating position.

The advantage of the invention that both bodies remain in heat-conducting contact even in the threading position and that a stable operating state is therefore reached in a matter of seconds even at the start of operation has an effect in particular if the entire heating chamber according to the invention over its entire length consists of the two Bodies exists and is formed by the narrow gap of the surface deformation that arises between the closing surfaces. This ensures that the two halves of the heating chamber maintain essentially the same temperature even in the threading position, that the temperature in the threading position drops only slightly or not at all, and that the operating temperature is reached again at the same time.

The two-part filament heating chamber can also be provided with recesses in its closing surfaces in the central region of its gap length, so that the clear width of the gap widens here. On the one hand, this can be useful in order to allow a certain ballooning of the thread and / or to avoid or reduce wall friction of the thread. On the other hand, this ensures that the pressure of the saddle steam is constant over the central area of the heating chamber. The central area provided with recesses can e.g. extend over 300 mm and less. The heating chamber according to the invention also proves particularly useful when one of the bodies, and preferably the stationary body, is provided with a so-called preheating channel - also referred to in this application as a “detour channel”. This is a channel which is introduced into the body essentially parallel to the surface deformation and which is fed with saturated steam. This preheating duct can simultaneously have stub lines in the thread guiding duct and thus be part of the steam feed line. The preheating channel has the advantage of heating the body into which it is inserted. However, it only proves its worth in that, according to the invention, the movable body remains in contact with the heated body even in the threading position and the heat is also transferred to this body. The preheating duct therefore leads only in connection with the invention to a decisive improvement in the heat management and the stability of the operating behavior of the heating chamber.

The joints between the closing surfaces can be made so tight both by suitable manufacturing techniques and by applying large clamping forces that no unacceptable losses of the heating medium have to be feared.

Sealing by means of a sealing plate placed between the closing surfaces of the two bodies is out of the question, since such a sealing plate generally also has a heat-insulating effect and therefore impedes the temperature balance between the two bodies.

According to the invention, two sealing strips are used to seal the heating chambers, which extend along and on both sides of the thread channel at a certain distance (e.g. 5 mm). Sealing strips or other transverse seals can also be provided in the inlet and outlet area of the heating chamber transversely to the thread channel. Without these sealing strips, the two bodies would have to be pressed very firmly against one another with their closing surfaces in order to seal the thread channel. This is disadvantageous in itself, but has the particular disadvantage that, if the thread channel is completely sealed, the amount of heat for heating the two bodies - apart from a possibly existing preheating channel - would have to be transported exclusively via the narrow thread channel.

In contrast, these sealing strips have the advantage that a separating joint of defined and predeterminable area is formed on both sides of the thread channel, into which the heating gas, in particular saturated steam, can penetrate without being able to escape. As a result, the delimiting closing surfaces on both sides of the thread channel are also heated. Therefore, this measure also serves for the uniform and rapid heating of the two bodies forming the heating chamber and for the stability of the operating behavior.

Pneumatic pressure can be used to seal the heating chamber, in particular the parting line, by means of which one or both bodies, on their rear side facing away from the heating chamber, are subjected to the pressure of a gas on a defined surface directly or by means of pressurized expansion bodies. The pressurization can be carried out with a foreign medium, e.g. Compressed air, happen. The pressurization is preferably carried out with the saturated steam itself. According to the invention, the area exposed to saturated steam in the area of the heating duct is smaller than the area exposed to saturated steam on the rear. For this purpose, sealing strips can also be provided on the rear side with saturated steam, which enclose an area which is larger than the area enclosed between the sealing strips in the area of the thread channel.

The pressurization of a body with a pressure cushion of the saturated steam itself, in addition to the pressure, has the particular advantage that at least one of the bodies forming the heating chamber, preferably the one that is movable and not provided with a preheating channel, also on that of its closing surface opposite side is heated, so that a possibly low temperature gradient occurs across the cross section of this body.

The advantage of the heating chamber according to the invention is, in particular, that the thread can be threaded easily, quickly and safely and that the sealing system, in particular sealing strips and pressing on the body of the heating chamber, brings about a complete seal. The problem-free threading on the other hand made it possible to make the narrow, gap-shaped end regions very narrow - limited only by the thread titer - and for any length. This almost completely prevents steam from escaping. Steam pressures of saturated water steam with temperatures up to over 200 ° C as well as a steady increase of the steam pressure from atmospheric pressure up to operating pressure and the steam temperature for the incoming thread and a steady decrease of the pressure up to atmospheric pressure and the temperature for the outgoing thread are made possible. The steady decrease in steam pressure also eliminates the risk of steam flow damaging the thread.

The width of the thread channel formed by the surface deformations is adapted to the thread titer, specifically in the end regions of the thread channel to a length of 100 to 300 mm, in order to achieve a good sealing effect. With an appropriate design of the width of the thread channel, it is possible to guide several threads in one thread channel. Likewise, a plurality of surface faults forming the thread channel can be provided on a body, one thread or several threads then being guided in each thread channel. The heating chamber according to the invention is therefore also suitable for heating thread sheets, e.g. in coulter drafters.

However, it is also possible to align a plurality of such filament heating chambers parallel to one another and to connect them to one another by means of a single line for the heating medium, in particular the saturated steam. Throttle losses between the thread channels are largely avoided and a good consistency of the thread temperatures achieved is guaranteed from one thread run to the other.

When heating above 100 ° C, the advantage of heat treatment of a running thread, in particular multifilament chemical thread, with saturated water vapor instead of strongly overheated water vapor or hot air is that the saturated water vapor has a large latent heat content (heat of vaporization) and because of the very high heat transfer coefficients Condensation - in contrast to convection, radiation or direct heat conduction - enables a strong heating of the thread at high thread speeds and short dwell times. Saturated steam treatment also results in a uniform temperature distribution and good temperature stability over the entire length of the treatment route. The treatment section can also be specified as desired by connecting several treatment chambers in series, since the required uniformity and constancy of the treatment temperature for several treatment chambers can be ensured by adjusting the pressure and by pressure equalization between the treatment chambers - with simultaneous removal of inert components. The losses at the entrance and exit of the treatment section can be kept low and lower than with comparable air heating sections if the thread entry and thread exit locks are designed accordingly.

Therefore, the saturated steam treatment chambers according to the invention, given the simple threading ability of running threads according to the invention, are particularly suitable for those thread treatments in which a large amount of heat has to be transferred to the thread at a high thread speed within a relatively short dwell time, as e.g. is the case with synthetic fibers in spinning processes, spin-stretching processes, spin-texturing or spin-stretch texturing processes and stretch texturing, draw twist, stretch winding and other stretching processes.

So it is e.g. possible, freshly spun fibers, which move at high speed e.g. more than 3000 m / min have been withdrawn from the spinneret, below the spinning shaft of a saturated steam treatment for tempering and / or - if necessary after the interposition of a stretch point fixation e.g. by thread brake - to subject to local stretching of the running thread. Since temperatures above 100 ° C and more than 220 ° C can be achieved, the length of the treatment section can also be influenced over a wide range.

In a continuous spinning-drawing process with drawing between two godets, the saturated steam treatment chamber can advantageously be used to apply the drawing temperature in a localized thread area between two godet units, the second godet unit usually being referred to as the drawing godet and being heated to approximately 120 ° C. The heating chamber according to this invention can also be used for fixing, tempering and / or shrinking the thread after the actual drawing.

Since friction false twists are now available for the highest thread speeds (US Pat. No. 4,339,915), the saturated steam treatment chamber according to the invention can also be used to spin a thread in a continuous process, in particular also polyester or polyamide threads, and then immediately - optionally with the interposition of a stretching zone or with simultaneous stretching - to be subjected to false twist treatment in the saturated steam treatment zone.

The advantage of saturated steam treatment is also that in saturated steam treatment, the thread is moistened due to the condensation of the steam into water. When leaving the filament heating chamber, there is therefore a very sudden evaporation of water as a result of the pressure relief, and thus the filament cools down to the boiling point of the water. Saturated steam treatment is therefore suitable for all processes in which thread heating and forced cooling follow one another directly, in particular for false twist texturing, in which case, according to the invention, by shaping the outlet gap and other measures already mentioned with the targeted pressure release, a temperature gradient in the sense of targeted cooling of the Thread is achieved.

To cool the thread to below 100 ° C after evaporation cooling by releasing the condensate, cooling by applying a thread preparation liquid or by applying water, e.g. by means of a nozzle. Water can also be introduced into the gap under pressure to provide enough water for condensation.

Finally, for the reasons mentioned, the saturated steam treatment chamber is also suitable for thread heating in a customary texturing or sequential or simultaneous stretch texturing process or for post-treatment of the thread textured by air jet treatment.

• Fig. 1-3 ein erstes Ausführungsbeispiel in zylindrischer Bauweise;
• Fig. 4-6 ein zweites Ausführungsbeispiel in zylindrischer Bauweise;
• Fig. 7-9 ein drittes Ausführungsbeispiel in zylindrischer Bauweise;
• Fig. 10-12 ein viertes Ausführungsbeispiel in zylindrischer Bauweise;
• Fig. 13, 14 ein fünftes Ausführungsbeispiel in zylindrischer Bauweise mit Einsätzen;
• Fig. 15a-15c, 16 ein sechstes Ausführungsbeispiel in zylindrischer Bauweise mit Druckabdichtungen;
• Fig. 17-20 Ausführungsbeispiele in Plattenbauweise;
• Fig. 21 die Anordnung einer Ventileinrichtung im Verbindungskanal von Vorheizkanal und Fadenkanal;
• Fig. 22 Ausführungsbeispiele in Plattenbauweise;
• Fig. 23, 24 bis 25 Ausführungsbeispiele mit Vorheizkanal, Kondensatabscheider und Inertgasabführung.

Exemplary embodiments of the invention are described below. Show it:

• Fig. 1-3 a first embodiment in a cylindrical design;
• Fig. 4-6 a second embodiment in a cylindrical design;
• Fig. 7-9 a third embodiment in a cylindrical design;
• Fig. 10-12 a fourth embodiment in a cylindrical design;
• 13, 14 a fifth embodiment in a cylindrical design with inserts;
• 15a-15c, 16 a sixth embodiment in a cylindrical design with pressure seals;
• Fig. 17-20 embodiments in plate construction;
• 21 shows the arrangement of a valve device in the connecting channel of preheating channel and thread channel;
• Fig. 22 embodiments in plate construction;
• 23, 24 to 25 exemplary embodiments with a preheating duct, condensate separator and inert gas discharge.

In Fig. 1, the heating chamber 2 is shown with the thread end 1 in section. It should be mentioned that the thread outlet end of the heating chamber can be designed accordingly. The steam feed channel into the heating chamber 2 is not shown. Saturated steam is produced under a pressure of e.g. 20 bar supplied so that a saturated steam temperature of approx. 210 ° C exists.

An outer body 4 (outer cylinder) is placed on the end flange 3 of the heating chamber 2. The outer body 4 is tightly clamped to the end flange 3, but - as will be explained later - a certain relative movement is possible. A seal (not shown here) can be placed between the end flange 3 and the outer body 4.

An inner body 6 is located in the inner bore 5 of the outer body 4. This inner body 6 is designed as a cylinder (inner cylinder) with a trapezoidal thread 7. The inner bore 5 of the outer cylinder has a meshing thread. The inner cylinder 6 with its thread is adapted to the inner bore 5 with its thread as tightly as possible. At the bottom of the bore 5 there is the sealing plate 8. It can be the same sealing plate that is also placed between the end flange 3 and the outer body 4 for the purpose of sealing.

As can be seen in particular from FIGS. 2 and 3, the end flange 3 has a hole 9 through which the thread emerges from the heating chamber. A corresponding hole is in the sealing plate 8. The jacket of the bore 5 in the outer body 4 cuts - seen in the projection onto a plane - this hole and has a groove 10 which - in the radial direction - through the Ge winch through the hole extends into the core and is aligned in the longitudinal direction with the hole 9 of the end flange. This groove 10 is provided as a thread guide groove (thread groove). The inner cylinder 6 has - as can be seen in FIG. 1 - a corresponding groove 11. This groove 11 only extends to the core of the inner cylinder 6. However, it can also extend into the core. The flanks 12 of the groove 11 are flared in the circumferential direction. The inner cylinder has a handle 13 with which the inner cylinder 6 can be rotated relative to the outer cylinder 4.

In the rotational position shown in Fig. 2 (threading position), the thread groove 10 in the inner jacket of the outer body 4 and the groove 11 in the thread and possibly the core of the inner body 6 (threading groove) form a wide threading slot through which the thread can be threaded. For pneumatic threading, the inner wall of the heating chamber 2 runs in a funnel shape towards the hole 9 in the end flange 3.

By turning the inner body 6 in the direction of the arrow, the threading groove 11 in the inner cylinder 6 is rotated into the position (operating position) shown in FIG. 6. As a result, the thread groove 10 used for thread guidance is reduced to a narrow gap, the width of which is so small that the heating gas or saturated steam losses and pressure losses are small. Because the flanks 14 of the thread groove 10, which are cut into the thread of the outer body, run essentially radially and because the flanks 12 of the threading groove 11 in the inner cylinder are flared, the thread is twisted along the flanks when the inner cylinder 6 is rotated 14 transported into the thread groove 10 serving the thread guide.

As can be seen from FIGS. 2 and 3, the outer body 4 is divided in a plane which lies between the center 15 of the inner cylinder 6 and the thread groove 10 in the outer body. A seal 16 is inserted into the parting plane, which is elastic and thicker than the spacers in the relaxed state. The two halves of the outer body are clamped together by screws 18 after the seal 16 and the spacers 17 have been inserted beforehand. Only then is the thread cut into the bore 5 of the outer body 4. This also provides the seal 16 with a thread. This causes the seal to seal the thread with the core and flanks on both sides of the thread groove 10 as a sealing strip. In order to allow the relative movement of the two halves of the outer body 4 on the end flange required by retensioning, the flange screws can be moved slightly in the elongated holes of the end flange 3. The spacers 17 can be made of a relatively soft metal, so that it is also possible to readjust the seal by pressing the spacers together. The spacers can also be missing. Your advantage is initially that the seal is set independently of the fitter during assembly. The sealing strips have the effect that the separating joint between the inner and outer cylinders in the area of the sealing strips is heated up by the heating gas / saturated steam spreading there, so that no temperature drop occurs in the area of the thread groove 10.

By rotating the inner cylinder 6 relative to the outer body 4, on the one hand, the overlap of the grooves 10 and 11 is eliminated, the groove 11 being rotated so far that it lies on the other side of the sealing plate 16. On the other hand, this rotation causes the inner body 6 to be screwed into the outer body 4 in such a way that it lies against the sealing plate 8 in a sealing manner with an axial force.

The exemplary embodiment according to FIGS. 4 to 6 has the inner cylinder 6, which is firmly connected to the flange 3, and the outer body 4 (outer cylinder) with a handle 13, which is rotatable around it.

The inner cylinder 6 has the groove 10 (thread groove) serving for thread guiding over its entire length. This thread groove 10 is expanded in the central region 19 in the circumferential direction and in depth, so that the actual heating chamber is created there, in which the thread can move, oscillate, balloon, without touching the walls, but in which, in particular, the saturated steam under a uniform pressure stands and therefore has a uniform temperature.

The outer cylinder 4 has a groove 11, which is made in the inner casing and the flanks 12 of which run gently from the bottom of the groove onto the inner casing.

The flange 3 has a hole 20, the front region 21 of which in the top view according to FIG. 5 covers the thread guide groove 10. The flanks 22 of the hole 20 are therefore flush with the flanks of the thread guide groove 10 in the top view according to FIGS. 5 and 6.

The outer cylinder 4 is divided and is clamped by the flanges 23 and screws 24 in such a way that the inner jacket closes tightly around the outer jacket of the inner body 6. In the parting plane of the split outer body 4, an elastic spacer plate 26, e.g. Sealing plate.

Longitudinal seals 25 designed as sealing strips are provided on both sides of the thread groove 10 in the inner cylinder 6, which seal the thread groove 10 and also its central region 19 in the circumferential direction.

The inner cylinder 6 has a central bore 27 serving as a preheating channel, which is closed at the top and communicates with the connecting pipe 28 at the bottom. Through the connection pipe 28, the bore 27 is charged with a pressurized heating gas, in particular saturated steam. The preheating channel 27 is connected to the thread groove 10, in particular its central region 19 through holes 29.

In operation, an axial force is applied to the outer cylinder 4 in the direction of arrow 30. In the case shown, a trapezoidal thread 31 is used for this purpose, which is attached in the upper region of the outer cylinder 4 and inner cylinder 6. By turning the outer cylinder 4 relative to the inner cylinder 6 by means of a handle 13, the outer body 4 is pressed against the sealing plate 8 on the end flange 3 in a sealing manner. In this rotational position (operating position), the groove 11 of the outer body 4 has the position shown in FIG. 6. The groove 11 is therefore located behind the sealing lips 25, so that no pressure medium, heating gas or saturated steam can get into the groove 11 from the thread groove 10. The thread groove 10 is limited by the inner wall of the outer cylinder 4 to a very narrow gap, which prevents the uneconomically large amounts of the pressure medium from escaping. Gap widths are on the order of less than 0.5 mm.

By turning the outer cylinder into the position shown in FIG. 5 (threading position), the groove 11 of the outer cylinder is brought into a position in which it covers the hole 20 in the flange 3 in the vertical direction and the thread groove 10 in the radial direction . This creates a large threading opening through which the thread can be threaded pneumatically or by means of a bristle or similar means.

The exemplary embodiment according to FIGS. 7 to 9 largely corresponds to that shown in FIGS. 4 to 6. The heating chamber consists of a tubular inner cylinder 6 with thread groove 10. The thread groove 10 is narrow in the thread inlet part 1 and in the thread outlet part and widens in the central region 19. The inner cylinder 6 is fixed in place on the flange 3. Its central bore, which serves as a preheating channel 27, is connected to steam line 28 with saturated water vapor. The water vapor can escape through the holes 29 into the enlarged central region 19 of the thread groove 10. The inner cylinder 6 is surrounded by an outer cylinder 4, which has an insertion gap 32 (slot) for the thread. The outer cylinder 4 is surrounded by bandages 33 to increase the strength. The outer cylinder 4 can be rotated by means of a handle 13.

In the position shown in FIG. 8 (threading position), the insertion gap 32 opens radially on the thread groove 10. It should be mentioned that the insertion gap 32 can also be directed secantial to tangential. In the second rotational position (operating position) shown in FIG. 9, the jacket is rotated such that the thread groove 10 is covered by the inner circumference (closing surface) of the outer cylinder 4.

A further special feature compared to the exemplary embodiment according to FIGS. 4 to 6 is that the inner cylinder 6 also has the transverse seals 34 at the thread inlet and thread outlet in addition to the longitudinal seals 25. These cross seals can be O-shaped sealing strips that extend from one longitudinal seal to another. However, it can also be an O-ring which surrounds the entire inner part 6. Likewise, the sealing strips 25 and transverse seals 34 can be formed in one piece as a ring or rectangular window. The sealing strips and cross seals are placed in the grooves of the inner cylinder (or the outer cylinder) so that they do not slip due to the relative movement of the cylinders. The grooves are only so deep that the sealing strips protrude beyond the closing surface of one body and lie in the operating position of the two bodies in a sealing manner on the closing surface of the other body (applies to all exemplary embodiments).

By using the transverse seals 34 according to the exemplary embodiment 7 or 10, it becomes superfluous to press the outer jacket 4 against the sealing plate 8 by axial force, as is shown in FIG. 4.

Furthermore, the inner cylinder 6 has on its rear side the longitudinal seals 35 shown in FIGS. 8 and 9 and, in each case at the thread inlet and thread outlet, a transverse seal that is not visible here (corresponding to the transverse seals 34 on the front side). The area between these longitudinal seals 35 and their transverse seals is charged via line 36 with the heating medium, here the saturated steam from tube 27. Since the secantial distance between the longitudinal seals 35 on the back of the inner cylinder 6 is greater than the secantial distance of the sealing strips 25 on the front of the inner part 6, in the operating position according to FIG. 9 the vapor pressure presses the movable outer cylinder 4 in the direction of arrow 37 against the longitudinal seals 25 on the front. On the one hand, this results in a secure sealing of the thread groove 10 and the surface area circumscribed by the sealing strips 25 and the transverse seals 34. Above all, however, the heating gas / saturated steam cushion on the back serves for the additional heating of both the inner and especially the outer cylinder.

10 to 12, the cylindrical inner part 6 (inner cylinder) is in turn firmly attached to the flange 3. The outer part 4 is in turn designed as a rotatable jacket 4 (outer cylinder) provided with an insertion gap 32. The insertion gap 32 opens into the thread groove 10 in the one rotational position (threading position) (not shown). In the other rotational position shown in FIGS. 11 and 12 (operating position), the jacket 4 covers the thread groove 10.

In the inner cylinder 6 a through-going groove 38 is made, which preferably has the same width and depth over its entire length (insert groove). Insert pieces 39 and 40 are inserted into the groove 38. The inserts 39 form the thread entry part and thread exit part and have a narrow thread groove 10, as shown in FIG. 11. The insert part 40 forms the central region 19 of the thread guide groove and can accordingly have a thread guide groove with an enlarged cross section, as shown in FIG. 11. The inserts 39 and 40 are sealed along their entire length by longitudinal seals 25 on both sides of the groove. The Flanks of the insert pieces are sealed on both sides by sealing strips 41 with respect to the insert groove 38. In order to achieve a certain degree of sealing mobility, the flanks of the insert groove and the insert parts are aligned parallel to one another.

The insert 40 of the central area 19 has on its rear side a longitudinal groove 42 which is penetrated by the holes 29 through which the thread groove 10 of the central area 29 is connected to the central bore 27 serving as a preheating channel for steam supply. Since the secantial distance of the sealing strips 25 on the thread groove side of the insert parts 40 is smaller than the secantial distance of the sealing strips 41, the insert piece 40 is pressed against the inner circumference of the jacket by the vapor pressure.

The inserts 39 have - as already described for the exemplary embodiment according to FIG. 7 - the transverse seals 34. The inserts 39 at the thread inlet and thread outlet can, but do not have to, be provided with a longitudinal groove 43 on their rear side which is acted upon by steam pressure. Likewise, it is not absolutely necessary to provide a separate steam duct for steaming the longitudinal groove 43. Rather, the vapor pressure from the longitudinal groove 42 of the insert 40 will provide sufficient vapor pressure also on the back of the insert 39. Even if the longitudinal groove 43 is not present or extends over only a short area from the insert 40 to the thread inlet or thread outlet, the vapor pressure forming behind the insert 39 is sufficient for the sealing lips 25 to be pressed sufficiently against the inner circumference of the jacket 4 to worry. It should be taken into account that a flow corresponding to the pressure drop occurs in the thread inlet and thread outlet, so that the static pressure on the back of the insert 39 is greater than the static pressure on the front of the insert. In addition, the sealing strips 41 also ensure that the rear side is sealed in a vapor-tight manner in the case of the insert pieces 39.

As can be seen from FIG. 10, the end faces of the insert groove 38 are sealed by the sealing plates 44 which are firmly fitted and sealed into the insert groove 38 at the ends. Sealing plates can also be used which lie tightly on the end faces of the inner cylinder.

In the embodiment according to FIGS. 13, 14, in particular the thread inlet part and the thread outlet part of the heating chamber are formed by a plurality of relatively thin insert pieces 45. For this purpose, the inner part 6, as is also shown in FIGS. 7 and 10, has an insert groove 38. The flanks of this insert groove 38, as can be seen in FIG. 14, are shaped convergingly in such a way that they provide support on both sides of a sealing lip 25 .

The heating chamber can also consist of an insert 40 in its central region. It can be seen that this insert 40 is also missing or can be replaced by individual shorter inserts.

The insert pieces 45 and 40 have flanks which are also adapted to the sealing lips 25. As a result, the inserts can be clamped between the sealing lips 25. Since there is a distance between the sealing lips, a static pressure will occur below the sealing lip, while a flow will arise above the sealing lips with a corresponding reduction in the static pressure. As a result, the sealing lips in this exemplary embodiment are also pressed forward against the inner circumference of the jacket 4.

In the exemplary embodiments according to FIGS. 10 to 14, the insert parts can consist of particularly wear-resistant materials, such as Ceramics, especially sintered ceramics or sintered metal. The advantage of this design is that the inserts can be easily removed if the thread titer to be processed is worn or changed. Furthermore, the inserts are easy to manufacture in bulk, while the manufacture of a wide groove in the inner cylinder 6 requires less manufacturing effort than the manufacture of a very fine thread groove.

The exemplary embodiments according to FIGS. 15a, 15b are characterized in that the pressing force of the inner cylinder 6 against the inner wall of the outer cylinder 4 does not take place directly as in FIGS. 8, 9, but instead by insert pieces 46, which are located on the rear side of the inner part 6 in an insert groove 47 are inserted. This insert groove 47 is pressurized from the bore 27 via bore 48 with steam pressure. In Fig. 15a, the longitudinal seals 49 and transverse seals are again provided, which seal the insert 46 against the groove flanks. It should be mentioned that there are also corresponding transverse seals, which, however, cannot be represented in the given views. Depending on the area ratio of the area, which is predetermined on the front side of the inner part 6 by the sealing strips 25 and the corresponding transverse seals, to the area which is predetermined by the sealing strips 49 and the corresponding transverse seals, the insert pieces 46 can be more or less extend less great length of the inner part 6. 16 shows that the insert extends over a partial length and has a feather-shaped cross section. Here, an annular O-ring can be used as a longitudinal and transverse seal. In the further partial illustration according to FIG. 16, the insert groove 47 with the insert 46 is cylindrical.

The insert pieces can also be rubber plugs, as shown in FIG. 15b, which are inserted sealingly into the insert groove 47.

15c shows that the insert 46 consists of a hose or expansion body which extends over an at least certain length in the insert groove 47 and which also a pressure medium, preferably saturated steam, is pressurized via a suitable connecting line, not shown here.

A double filament heating chamber is shown in FIG. The filament heating chambers consist of the plates 51, 52 and 53. The plate pair 51 and 53 and the plate pair 52 and 53 each form a filament heating chamber.

Each plate 51 and 52 has the two planes 73 and 74 which are plane-parallel to one another and are connected to one another by a step 54. The plate 53 is displaceable between the plates 51 and 52. The plate 53 also has the plane-parallel planes 75 and 76, which are connected to one another by the steps 55. The steps 54 and 55 of the plates 51, 52 and 53 are each of the same size. In the exemplary embodiment it is shown that the steps form a plane. However, a different level training is also possible. In particular, it is possible to make the steps concave - in the cross section shown. It is also possible to slightly bend the steps in the thread running direction so that the thread is guided in contact with a step. Likewise, curved surfaces can be provided instead of the planes in the thread running direction, so that the thread is guided in contact with a surface. In both cases, a curved thread channel is created.

The plate 53 is slidably guided with its levels 75, 76 between the mutually facing levels 73, 74 of the plates 51 and 52. In the position shown in FIG. 17 (threading position), a longitudinal slit is created on the front of the plates 51 and 52 in the area of the steps 55 of the plate 53, since this step 55 slightly projects above the front of the plates 51, 52. Through these longitudinal slots, a thread running parallel to the longitudinal slots can be inserted transversely to its running direction into the gap between the plates 51 and 53 or 52 and 53. The plate 53 is then pushed back into a position which is indicated in FIG. 18a (operating position). In this position, two narrow, parallel, straight or possibly curved thread channels are created. Each thread channel is formed by the plane 74 and the step 54 of the plate 51 and 52 and by the plane 75 and the step 55 of the plate 53. The two thread channels are fed with saturated water vapor through steam connection 61 and channel 58 and intermediate channel 60. For this purpose - as can be seen from FIGS. 18a, 18b - in the area of the mouth of the steam channel 58 and the steam passage channel 60, a recess 77 is machined into the plane 74 and the step 54 of the plates 51 and 52, respectively. This recess causes an expansion of the thread channel. In this case, this expansion serves to allow the steam flowing through steam channel 58 to flow unthrottled into channel 60, so that the same pressure and temperature conditions exist in the two adjacent thread channels. However, it is also possible to provide the recess 77 over a greater length, so that the narrow gap only remains in the inlet and outlet region of the thread 59. It should be mentioned that the gap width there is approximately 0.2 to 0.3 mm with a length of the end regions of 60 mm and more. This means that a thread of 167 dtex can be treated with saturated water vapor without damaging wall friction with only slight steam losses at temperatures of 220 ° C, corresponding to a pressure of 24 bar.

The plate pack consisting of plates 51, 52 and 53 is surrounded on all sides by insulating material 62. This plate package is enclosed in a solid block (housing), which is screwed together from the plates 64, 65, 66 and is stable enough to absorb the pressures generated in the interior of the thread channel and the forces caused thereby. In order to compress the plate pack, the hose / expansion body 68 is nestled into a chamber 67 of the plate 66, which extends essentially over the entire length of the heating chamber. The hose preferably has an elongated cross section, so that the width with which the hose rests on the side surface of the plate 52 is greater than the width of the thread channel in the operating position. The hose 68 can therefore be subjected to a pressure that is approximately lower by the area ratio in order to compress the plate pack 51, 52, 53 in a vapor-tight manner.

The hose 68 is either connected to the company compressed air network. However, it is preferred to connect the hose 18 to the saturated steam line network. For this you can e.g. fill the hose 68 with a liquid which in turn is pressurized by the saturated steam. In order to achieve the previously described advantages of additional heating, especially of the plate, which has no preheating channel, the saturated steam itself is preferably applied to the hose.

The balls 63 transmit the forces applied to the plate pack 51, 52, 53 by the hose to the plate 64 of the solid block (housing).

To seal the thread treatment chamber there is at least one sealing strip 56 or 57 on each pair of levels, which is flexible within limits. By means of these sealing strips, which extend along the step, it is avoided that the surface pairing 73, 74 of the plate 51 and the surface pairing 75, 76 of the plate 53 have to be manufactured with absolutely precise dimensional accuracy. Above all, these sealing strips also allow a defined surface area to be created between the levels, into which the heating gas / saturated steam can penetrate for the purpose of additional heating. To seal this surface area in the thread running direction, transverse seals can also be provided at the thread entrance and thread exit, which extend between the longitudinal seals. This transverse seal is also achieved in that the longitudinal seals have extensions at their ends that extend to or close to the thread channel or the respective step.

The middle plate 53 is adjusted by cylinder-piston unit 70, 71 by means of piston rod 69. With 72 a stop screw is designated, through which the gap width of the thread treatment chamber can be adjusted during operation.

The embodiment according to FIGS. 19, 20 and 20a shows the left plate 51, the right plate 52 and the middle plate 53 in longitudinal and cross section. The structure largely corresponds to that of the embodiment according to FIGS. 17, 18.

The following deviations are noteworthy: The outer plates 51 and 52 are designed as flat plates. An intermediate plate 78 is placed on each of these plates, which corresponds in thickness to the step in the inner plate 53. This results in manufacturing simplifications.

Furthermore, the steam supply duct (intermediate duct) 60, which penetrates the middle plate 53 between the two stages 54, 55, is connected to a steam duct 79, which penetrates the parting plane between the plates 51, 52, 53 and intermediate plates 78, and which extends from the steam connection 61 is fed via a detour channel 80. Detour channel 80 extends along step 54. A further detour channel 81 is provided in the other plate 52, which extends along step 55 and is connected to steam channels 79. The detour channels serve as preheating channels for the plates 51, 52. As can be seen from FIG. 20, the detour channel 80 is connected to the steam connection 61 at the top. Furthermore, the detour channels 80, 81 are connected at their lower end to condensate drain lines 82. The condensed water, which collects at the bottom of the detour channels 80, 81, reaches a collection container via throttles 82.1, in particular adjustable throttles, and is returned to the steam generator by a pump. Automatic, preferably thermostatically controlled, condensate drain valves are preferably connected to the outlet of the detour channels 81, 82 and ensure constant condensate drainage. They are not shown in the drawing, as are the condensate collector and the condensate pump in the feed line to the steam generator.

The described steam supply system has the advantage that the steam supply is automatically interrupted when the middle plate 53 is pulled out of its operating position. Furthermore, there is the advantage that - in the exemplary embodiment shown - at least the detour channel 80 is also acted upon with the saturated water vapor in the thread insertion position of the middle plate 53, with the advantage that the side plate 51 does not cool down, particularly in the area of the step 54. The supply of the detour channel 81 with the saturated steam can also take place in the threading position of the middle plate 53 via an additional channel 83 shown in broken lines, which in the thread insertion position of the middle plate 53 is aligned with the part of the steam channel 79 in the right plate 52 which leads to the detour channel 81 . This additional duct 83 would also ensure that the detour duct 81 is supplied with saturated steam in the thread insertion position of the middle plate 53. The supply of saturated steam to the detour channels in the threading position offers the advantage in connection with this invention that all the bodies / plates forming the heating chambers are heated further by the continuous surface contact. This also applies to the other exemplary embodiments.

It can be seen from the longitudinal section according to FIG. 20 that the thread groove formed by the steps 54 and 55 widens in the central region 19 of the heating chamber.

It has already been mentioned in connection with FIGS. 17, 18 that the plate pack is held together by external forces. These external forces are indicated here by arrow 84. These external forces must be so great that the frictional force between the plates 51, 52 on the one hand and 53 on the other hand exceeds the steam force acting on the plate 53. In order to achieve a particularly solid construction, the heating chamber has the crossbeams 85.

21 shows schematically how the preheating channels 27 of the heating chamber described above can be connected. The preheating ducts 27 of a plurality of heating chambers of the same type are connected at the bottom by means of connecting pipes 28 to a common steam generator 86 with suitable heating devices 94, for example electrical resistance heating pipes. The connecting pipes 87 serve both the steam supply and the condensate return. For this purpose, they are laid on a slope and have a large cross-section.

According to FIG. 21, a shut-off device designed as a needle valve 90 is now installed at the upper end of the steam supply pipe 88, in such a way that on the one hand the preheating duct 27 is constantly fed with saturated steam and heated to the temperature of the saturated steam, but this steam is only via the valve 90 gets into the thread channel. For this purpose, the connecting pipe 29 is connected to the valve seat 92 of the housing 93 in a pressure-tight manner. Connecting channel 29 corresponds to holes 29 and 79 in FIGS. 4 to 20. The valve can be operated from the outside. The arrangement is such that the valve seat 92 is only released or opened by the axially movable, concentrically arranged valve needle 91 when the thread channel 10 is closed radially by relative rotation of the two cylinders 4 and 6, i.e. the thread heating chamber is brought into the operating position. In contrast, in the threading or inserting position of the thread channel 10 - corresponding to FIGS. 2,4 / 5,7 / 8 and 10 - the needle valve 90 is completely sealed, so that steam cannot escape.

This is necessary to protect the operating personnel against accidents. To additionally Be To rule out service errors, the valve stem is led out from the heating chamber in a pressure-tight manner via control cams of a logic circuit, not shown in detail. This results in a coupling or synchronization of the two movements, taking into account the design required dead paths, for example from the distance of the sealing strips 25 on both sides of the thread guide channel 10. The connecting pipe 29, which is bent upwards in the manner of a siphon and begins at the top in the preheating channel, has the advantage that through this connecting pipe Inert, non-condensable gases that collect in blind holes and other areas without flow are constantly removed.

It should be mentioned that it is also possible to arrange the shut-off element in the steam supply pipe 88 at the bottom. However, this has the disadvantage that possibly non-condensable, inert components of the heating medium, such as air or the like, collect at the top in the steam supply pipe 88 and lead to temperature differences from one pipe 88 to the other over time, unless a separate exhaust duct for inert gases is provided .

Furthermore, the common steam generator 86 can also be connected to the steam supply pipes 88 at the top. However, this requires the attachment of separate condensate return lines at the lower end of the preheating duct, possibly with a condensate pump to the steam generator.

Finally, it should be mentioned that, in the example shown in FIG. 21, in addition to the refluxing condensate, the common steam generator must constantly be supplied with a certain amount of feed water in order to replace the heating medium which is dragged out of the thread heating chamber by the treated thread (humidification). This is preferably done by a feed water pump (pressure booster pump), not shown, which is controlled by a high pressure float or the like.

22a shows a heating chamber in cross section, which likewise consists of two flat plates 51 and 53. These plates are displaceable relative to one another parallel to their surface by cylinder-piston unit 69-71. In one end position (threading position), the front edge 105 of the plate 53 recedes behind the thread groove 10, so that an opening is created in which the thread can be inserted. In the other relative position (operating position) shown in dashed lines, the thread groove 10 in the plate 51 is closed by the closing surface of the plate 53. In the closed state, the thread channel thus formed is fed with saturated steam by opening a valve (not shown here) via preheating channel 80 and bore 58. The back of plate 52 is also charged with steam through bore 103. As a result, the plate 52, which is sealed off from the housing 104 by circumferential seals 49, is pressed against the other plate 53, so that these plates, at least with their seals 56, lie on one another in a vapor-tight manner. It is particularly important that the surface area circumscribed by the surrounding seals 49 is larger than the surface area formed by the longitudinal seals 56, 57 and the associated transverse seals. This type of pressure also heats the housing 104, which in turn helps to standardize the temperature of all parts of the heating chamber.

24d shows a similar embodiment, which differs from that in FIG. 24a in principle only in that the front of the plate 51 is provided with a step 108.

The exemplary embodiment according to FIG. 24c is also essentially similar. Its main difference from the explanations according to FIGS. 24a and 24d is that the plate 53 does not open a threading slot above the thread guide groove in the one threading position, but rather has an enlarged longitudinal groove 109 (threading groove), which in the threading position shown, in which the heating chamber except Operation is with the thread groove 10 aligned and forms an extended threading gap through which the thread can be easily threaded pneumatically or by means of bristles. The threading groove 109 is provided on one side with a bevel so that the thread is pressed into the thread guide groove 10 by the bevel when the plate 51 is moved into its operating position shown in dashed lines.

In all of these exemplary embodiments, it is necessary that the housing 104, which surrounds the plates 51, 52 forming the heating chamber on at least two opposite sides in the case of the exemplary embodiment according to FIG. 24c, is designed to be stable and rigid enough to withstand the steam forces and to ensure, even when loaded with the steam pressure, that the plates lie close together in their contact surfaces and with their longitudinal and transverse seals.

20 and 20a, the steam connection 61 is shown in the left plate, which opens into the upper region of the preheating duct 80. The condensate drain line is designated 82 and starts from the lower part of the preheating duct 80. An orifice or throttle 82.1 is provided, through which condensates and inert gases, which collect in the lower sack-shaped part of the preheating chamber 80, can slowly escape. 20a shows that the preheating duct 80 extends to the end of the side plates 51, 52 and is closed there with a stopper, which has a narrow slot-shaped groove 82.2 with blind holes 82.3 along its length.

Other condensate separators, in particular temperature-operated condensate separators, are known in the literature (for example Dubbel, “Taschenbuch für den Maschinenbau”, 14th edition, page 500/501). A preferred exemplary embodiment of a condensate separator is shown in FIG. 23. The heating chamber shown there, like the exemplary embodiments according to FIGS. 4 to 16, consists of the stationary, tubular inner cylinder 6 and the outer cylinder 4 which can be rotated around it. For details of the construction, reference can be made to FIGS. 4 to 16 in this respect. The preheating duct 27 formed in the interior of the inner cylinder 6 is charged with steam at its upper end via steam connection 61. The holes 29, through which the saturated steam from the preheating duct 80 reaches the central region 19 of the thread duct 10, are arranged in the upper region of the preheating chamber. This creates a sack in the lower area of the preheating duct, in which condensate, but also inert gases, ie gases and vapors that do not condense under the given pressure and temperature conditions, collect, in particular those gases that are heavier than saturated steam. The condensates, in particular the condensed water and the inert gases, have a temperature which is below the temperature of the saturated steam. The preheating duct has an opening 106 at the bottom, which opens into a separation chamber 107. Another opening 110 of the separation chamber 107 leads to the outside or to a condensate collector, which is not shown here. The opening 106 and the opening 110 both lie in a common plane. On the bottom of the separation chamber 107 there is a plate 111 which is freely movable here, but which can also be supported by a weak spring. It is important that the plate lies essentially parallel to the plane of the openings 106, 110 and is only a short distance from this plane. On its underside, the plate has spacers 112, which have the effect that the static pressure of the separation chamber 107 also acts on the underside of the plate.

It can be assumed that when the heating chamber is heated up, condensates initially collect in the lower sack-shaped region of the preheating chamber 80. These condensates are conveyed to the condensate collector via openings 106, separation chamber 107 and opening 110.

After the heating has ended, only a small amount of condensate remains, so that saturated steam begins to flow out through the openings 106 and 110. The saturated steam flow hits the plate 111 so that it flows to the opening at a high flow rate. As a result of this high flow rate, the static pressure on the top of the plate drops, while the static pressure remains on the bottom of the plate. As a result, the plate is pressed against the two openings 106 and 110 and the separating chamber 107 is closed, so that the static pressure is maintained there. Since the closure area at the openings 106 is smaller than the underside of the plate 111 and since there is essentially no pressure higher than atmospheric pressure at the opening 110, the plate lies stably in front of the opening 106.

This state remains as long as the temperature in the deposition chamber 107 is maintained. If condensate or inert gases collect again in the lower sack-shaped area of the preheating chamber 80, the temperature drops. As a result, the pressure in the separation chamber 107, which takes part in the temperature fluctuations of the preheating channel as a result of the direct heat-conducting connection to the inner body 6, also drops. As a result of the resulting excess pressure at the opening 106, the plate first opens the opening 106, as a result of which the plate tilts in relation to the opening 110. As a result, the pressure in the separation chamber 107 drops and the plate 111 falls to the bottom, so that the condensate or the inert gases can now escape completely. In the illustrated embodiment, the plate is vertically movable against its gravity. It is also possible to guide the plate horizontally or pivotably and / or the effect of gravity by e.g. To replace spring force.

24 with cross section according to FIGS. 25a, 25b largely corresponds to the heating chamber according to FIGS. 7 and 8 or 9. It consists of a tubular inner cylinder 6 with thread groove 10. The thread groove 10 is in the thread inlet part and in the thread outlet part narrow and widening in the middle region 19. The inner cylinder 6 is fixed between the flange 3 and the flange 113. Inside, the inner cylinder 6 has a central preheating channel 114 in its lower region, which is only indicated by dashed lines here. This central heating channel is permanently connected to the steam supply line 115. This has the effect that the inner cylinder 6 is constantly heated in its middle and lower part.

In its upper part, the inner part 6 has a steam supply duct 27, which also serves as a preheating duct and communicates via hole 29 with the central region 19 of the thread groove 10. On the rear side, the steam supply channel 27 preferably communicates with a steam pressure zone, which is formed between the outer cylinder 4 and the inner cylinder 8 - as also shown in FIGS. 8 and 9 - between the sealing lips 35. This pressure zone, which is fed with the pressurized heating gas, in particular saturated steam, during operation, causes the outer part 4 and the inner part 6 in the area of the thread guide groove and the sealing strips 25 to be pressed tightly against one another, so that a sealing lip 25 is used sufficiently tight sealing of the heating area is given. Above all, in this pressing zone between the sealing lips 35, the outer part 4 is heated, which comes into direct contact with the heating gas or saturated steam in this zone.

The layout of the steam duct 27 and the hole 29, i.e. the saturated steam flow from top to bottom means that no condensate can accumulate in the steam supply channel 27.

The steam supply to the steam supply duct 27 takes place via the steam connection line 28 and the 3-way valve 116. The steam supply duct 27 is optionally supplied with or relieved of steam by this valve. Through the discharge also relieves the pressure on the back of the inner part 6 at the same time, so that the outer part 4 can be easily rotated relative to the inner part 6 into the threading position according to FIG. 25a. Even in this threading position, however, the steam supply to the lower central preheating channel 114 is maintained.

With 117 a discharge pipe is designated, which sits concentrically in the central preheating channel 114 and extends to its upper region. The discharge pipe is led out of the bend of the supply line 115 and closed by a narrow throttle 118, which serves as a condensate separator. A small amount of steam or condensate or inert gases can constantly escape through the throttle 118, so that the discharge pipe 117 prevents inert, non-condensable gases from collecting in the upper region of the central heating duct 114. The condensates themselves collecting at the bottom of the preheating duct can run back to the steam generator in line 115. Possibly. a condensate separator can also be arranged in line 115, e.g. of the type described in connection with FIG. 23.

Claims (50)

1. Heating chamber for threads in motion, in particular synthetic threads, in which the threads are treated with saturated steam at more than 2 bar and the end regions of which have two bodies (4, 6; 51, 53) displaceable relatively to one another, which in their operating position lie in contact with each other over their substantially congruent surface regions (closing surfaces) and as a result of a surface deformation in the surface of one of the two bodies enclose between them a thread channel (10) which is closely adapted to the cross-section of the thread and through which the thread runs in the longitudinal direction, characterised in that

1.1. the two bodies (4, 6; 51, 53) each have a surface deformation parallel to the other in the form of pairs: groove (10) - groove (11); groove (10) - end edge (105); or step (54) step (55);

1.2 the closing surfaces of the two bodies are displaceable transversely to the surface deformation between the operating position and a threading position as they slide over one another;

1.3 and the surface deformations of the two bodies cover each other in the threading position so that the thread channel (10) is increased in width for the purpose of inserting a thread in its direction of travel or is open in a longitudinal plane for the purpose of inserting a moving thread transversely to its direction of travel.

2. Heating chamber according to claim 1, characterised in that the bodies and the surface deformations extend over the whole length of the heating chamber.

3. Heating chamber according to claim 2, characterised in that the surface deformations are increased in width in the middle region while in the end regions they are adapted to the titre of the thread or to the sum of the titres of all the threads travelling together inside the surface deformations.

4. Heating chamber according to claim 1, characterised in that the bodies and the surface deformations extend only over the end regions of the heating chamber and in that the heating chamber is increased in cross-section in the middle region (in particular Figs. 1-3).

5. Heating chamber according to one of the claims 1 to 4, characterised in that the depth and/or width of the groove or step measures 0.2 to 0.5 mm in the end regions which extend over, preferably, 100 to 300 mm.

6. Heating chamber according to one of the claims 1 to 5, characterised in that the thread channel (10) is of such dimensions that it can carry a plurality of threads.

7. Heating chamber according to one of the claims 1 to 6, characterised in that several grooves or steps are formed on the thread guiding body to carry a plurality of threads or thread bundles.

8. Heating chamber according to one of the claims 1 to 7, characterised in that a preheating channel (27, 80) extending over at least part of the length of the surface deformation and charged with saturated steam is provided in at least one of the bodies, preferably the fixed body.

9. Heating chamber according to claim 8, characterised in that the preheating channel (27, 80) is connected by connecting channels (29, 79) to the region of the heating chamber through which the thread travels.

10. Heating chamber according to claim 9, characterised in that the preheating channel (27, 80) is connected in its upper region with a steam attachment (28, 61) and in its lower region with a discharge duct (82) for condensate.

11. Heating chamber according to one of the claims 8 to 10, characterised in that the upper region of the preheating channel (114) has a closable and/or throttled (restrictor 118) discharge channel (117) for inert gases (Figures 24, 25 a, b).

12. Heating chamber according to one of the claims 9, 10, characterised in that the connecting channel (29) which opens into the heating chamber through which the thread travels is branched off the upper region of the preheating channel (27).

13. Heating chamber according to one of the claims 1 to 12, characterised in that sealing strips (25, 56, 57) are provided along the grooves (10) or steps (54, 55) and seal off the area of separation between the closing surfaces of the bodies.

14. Heating chamber according to claim 13, characterised in that sealing strips (34) are provided transversely to the surface deformation at the thread inlet and/or thread outlet of the heating chamber, which have a passage for the thread.

15. Heating chamber according to claim 13, characterised in that the sealing strips have portions of increased width in the region of the thread inlet and/or thread outlet, said portions extending up to or close to the grooves (10) or steps (54,55).

16. Heating chamber according to one of the claims 1 to 15, characterised in that at least one of the bodies (6, 51) is subjected on its rear surface remote from its closing surface to the saturated steam which is under the operating pressure.

17. Heating chamber according to claim 16, characterised in that one of the bodies is rigid (external body 4) and encloses the other body (cylinder 6), making close contact with it at the front and rear of the latter.

18. Heating chamber according to claims 16, 17, characterised in that the thread channel (10) of the heating chamber and the rear surface which is subjected to saturated steam can be synchronously relieved of the pressure of the saturated steam and are preferably connected to the steam attachment (61) preferably by way of a common three-way valve (116) which has a pressure relieved outlet.

19. Heating chamber according to one of the claims 1 to 15, characterised in that a recess (47) for an insert with an insert (46) imperviously enclosed therein is situated at the rear of at least one of the bodies, on the side of the body remote from the closing surface, and in that the base of the recess for the insert can be subjected to the saturated steam which is under operating pressure.

20. Heating chamber according to one of the claims 1 to 15, characterised in that a tube (68), expansion body or flexible pipe charged with a pressure fluid extends over substantially the whole length of the path of travel of the thread on the rear side of at least one of the bodies, remote from the closing surface, which tube, expansion body or pipe lies with three of its or their sides in contact with a chamber (67) which is open on one side, and bears against the housing (66) on the open side.

21. Heating chamber according to claim 20, characterised in that the tube (68) or expansion body is directly subjected to the saturated steam which is under pressure.

22. Heating chamber according to claim 21, characterised in that the tube (68) or expansion body is filled with a fluid, in particular a liquid with a high boiling point, which liquid is subjected to pressure, in particular the pressure of the saturated steam.

23. Heating chamber according to claims 1 to 22, characterised in that one or more inserts (39, 40) carrying the step or groove are situated in a recess (38) provided for an insert in the closing surface of one of the bodies.

24. Heating chamber according to claim 23, characterised in that the inserts (39, 40) are situated in the insert recess (38) so as to be sealed off perpendicularly to the closing surface and are subjected to pressure on their rear side, preferably the pressure of the steam which is under the operating pressure.

25. Heating chamber according to one of the claims 1 to 24, characterised in that the bodies are in the form of two planar or curved plates (51, 53) sliding over one another and having a rectilinear or slightly curved thread groove (10) in the closing surface of the first plate (51) to form the thread channel and a threading groove (11) parallel thereto in the closing surface of the second plate (53), which threading groove (11) combines with the thread groove of the first plate when in the threading position to form a thread channel of increased width for axial insertion of the thread and preferably has a greater cross-section than the thread groove and preferably continuously increases in width from its base to the closing surface, at least on one side.

26. Heating chamber according to one of the claims 1 to 24, characterised in that the bodies consist of two planar or curved plates (51, 53) sliding on one another and having a rectilinear or slightly curved thread groove (10) forming the thread channel in the first plate, which groove is covered by the closing surface of the other plate when the plates are in the operating position whereas in the position for threading the said groove is opened for the insertion of the moving thread by displacement of the end edge (105) formed on the closing surface of the second plate (53), the surface of said end edge preferably leaving an acute angle open between itself and the closing surface of the other plate (51).

27. Heating chamber according to one of the claims 1 to 24, characterised in that the bodies consist of two planar or curved plates (51,53) having rectilinear or slightly curved steps (54, 55) of equal size in their closing surfaces and in that in the operating position the steps forming a thread channel closely adapted to the cross-section of the thread while in the threading position they form a thread channel of greater width for axial insertion of the thread.

28. Heating chamber according to one of the claims 1 to 24, characterised in that the two bodies consist of planar or curved plates (51, 53) sliding over one another and having rectilinear or curved steps of equal size which in the operating position form a thread channel closely adapted to the cross-section of the thread, and in that one plate (53) is displaceable relatively to the other plate (51) so that the step (55) of that plate (53) lies above the other plate (51 or 52) in the threading position to form a gap for insertion of the moving thread, which gap can be closed by displacement of the plate (53).

29. Heating chamber according to one of the claims 1 to 24, characterised in that one body is in the form of an internal cylinder (6) and the other body is in the form of a rigid external cylinder (4) enclosing said internal cylinder as a jacket having the same diameter, and in that a groove (10,11) is formed on a generatrix or helical line of the internal cylinder and on the internal surface of the external cylinder, and in that the internal cylinder and the external cylinder are rotatable and/or axially displaceable in relation to one another so that the grooves cover each other in the threading position and form a thread channel of increased width for the purpose of axial insertion of a thread, the groove (11) provided as threading groove preferably having a larger cross-section than the thread groove and preferabiy increasing continuously in width from its base to the peripheral surface, at least unilaterally.

30. Heating chamber according to one of the claims 1 to 24, characterised in that the first of the two bodies is an internal cylinder (6) having a groove (10) on a generatrix or helical line; the second body is a rigid external cylinder (4) enclosing the internal cylinder in the form of a jacket the internal diameter of which is substantially equal to the external diameter of the internal cylinder and having a slot (32) along a generatrix or helical line, and in that the two bodies are rotatable and/or axially displaceable in relation to one another so that in the position for threading, the slot (32) is aligned with the groove (10) of the internal cylinder for placing the moving thread into position.

31. Heating chamber according to claim 30, characterised in that the external cylinder (4) encloses the internal cylinder (6) with a press fit and can be spread open in the region of the slot (32).

32. Heating chamber according to claim 29, characterised in that the external cylinder (4) is sub-divided in at least one longitudinal plane and in that the two halves are braced together in the longitudinal seam (26) in the sense of a reduction in their diameter (binding 33, screw fitting 24).

33. Heating chamber according to claim 32, characterised in that the external cylinder is sub-divided in a longitudinal plane and in that a flexible seal (26) is inserted in the longitudinal seam.

34. Heating chamber according to one of the claims 1 to 24, characterised in that the external body (4) is divided into two parts in a longitudinal plane situated between the centre (15) of the internal cylinder (6) and the thread groove (11) formed on a generatrix of the internal cylinder, and in that the two parts of the external body (4) can be braced against a sealing plate (16) situated between them, which sealing plate extends to the surface of the internal cylinder on both sides of the thread guiding groove.

35. Heating chamber according to claim 34, characterised in that spacer members (17) are inserted between the parts of the external body to limit the bias tension introduced into the sealing plate (16).

36. Heating chamber according to one of the claims 29 to 33, characterised in that the internal cylinder is fixed in position and is provided with the thread groove (10) and in that the surrounding external cylinder (4) is rotatable about the internal cylinder.

37. Heating chamber according to claim 13 in combination with claim 36, characterised in that the external cylinder (4) is rotatable relatively to the internal cylinder through an angle such that in the operating position, the groove (11) in the external cylinder lies outside the sector angle between the sealing strips.

38. Heating chamber according to claim 36 or 37, characterised in that the internal cylinder (6) is a closed tube at least over part of its length, the inside of which tube is connected to a steam pipe (28, 115) and constitutes the preheating channel (27,114).

39. Heating chamber according to claim 38, characterised in that the steam pipe (28, 115) and optionally pipe for condensate and optionally discharge channel (117) for inert gases are attached on one side only, preferably at the bottom to the preheating channel (27) of the internal cylinder and in that the external cylinder (4) is fitted over the internal cylinder (6) from the other side.

40. Heating chamber according to claim 29 or 30, characterised in that the internal cylinder (6) and external cylinder (4) are mounted on an end flange (3) of the heating chamber and in that the movable one of the two bodies is rotatable and longitudinally displaceable and when rotated into the operating position is pressed with an axial force (30) against the flange (3) of the heating chamber (2) to make sealing contact.

41. Heating chamber according to claim 40, characterised in that the internal cylinder and the external cylinder (4, 6) have a screw thread, in that the thread guiding groove (10) of the fixed cylinder extends to in that the threading groove of the rotatable body extends at least to the core.

42. Heating chamber according to claim 41 in combination with claim 34 or 35, characterised in that the screw thread is also cut into the sealing plate (16).

43. Heating chamber according to claims 40 to 42, characterised in that the internal cylinder (6) is fixed in position on the end flange and has a screw thread and has a thread groove (10) extending into the core and in that the external cylinder (4) also has a screw thread and a slot for insertion.

44. Heating chamber according to one of the claims 25 to 28, characterised by a stack of more than two identical plates (51, 52, 53) which make contact with one another in two plane parallel planes (73, 74 and 75, 76) in each case forming a surface deformation (steps 54, 55), adjacent plates being displaceable in relation to one another by a movement at right angles to the surface deformation.

45. Heating chamber according to claims 27, 28, characterised in that one of the plates (53) is provided on both sides with a pair (75, 76) of plane parallel closing planes (75, 76) connected by a step (55), and in that a similar plate (51 and 52, respectively) is provided on each of the two sides of the plate (53) to form two thread channels.

46. Heating chamber according to claim 45, characterised in that the two outer plates (51, 52) are fixed in position and the middle plate (53) is displaceably mounted.

47. Heating chamber according to claim 44, characterised in that the plate (53) arranged between two plates (51, 52) is penetrated by a channel (60) for saturated steam in the region of the step or groove.

48. Heating chamber according to one of the claims 27, 28, 45, 46, characterised in that the plates are pressed together by a contact pressure force and in that the friction of the plates (51, 52, 53) produced by the contact pressure against their closing surfaces is greater than the forces of the steam acting on the surfaces of the steps (55) which are perpendicular to the closing surfaces.

49. Heating chamber according to one of the claims 44 to 48, characterised in that the plates of a stack (51, 52, 53) are accommodated in a rigid housing (64,65,66; 104) which takes up the steam forces acting transversely to the closing planes of the plates.

50. Heating chamber according to claim 47, characterised in that the plates (51, 52, 53) are heat-insulated against the housing (64, 65, 66) (insulating plates 62).

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