JPH0460792B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION Field of Industrial Application The present invention is a spring spanner for large coil springs, especially vehicle axle springs, which has two loose coil springs.
each comprising a dish-shaped pressure plate with a central insertion opening, a threaded spindle with a spindle head having a spanner profile and a cylindrical threaded tube with an internal thread for screwing the threaded spindle, The threaded spindle is rotatably supported in a cylindrical guide tube by means of a thrust bearing, the guide tube having a radial support surface for supporting a pressure plate on the spindle head side; A threaded tube is axially movable and relatively rotationally connected to the guide tube by a form-locking guide element, and a radial thread is provided on the periphery of the end opposite the spindle head. In addition to a radial enlargement forming a passage opening for the fingers, a recess is provided on the outer surface in the edge region of the insertion opening of the pressure plate remote from the spindle head; is adapted to engage in this recess so that a relatively non-rotatable tensile connection is obtained between the threaded tube and the pressure plate.

PRIOR ART In known spring spanners of the type described above, an axially movable groove-key connection is used as a relative rotation prevention element between a cylindrical guide tube on the one hand and a similarly cylindrical threaded tube on the other hand. In one embodiment, the guide tube is connected to the threaded tube in a rotationally fixed manner by means of a radial projection which engages in an axial guide slot (see German patent no.
3304321 specification). In these two examples, the threaded tube can be slid telescopically within the guide tube. In one configuration, the threaded tube has at least one axial groove open at both ends on its circumference, in which a bar key or slide fastened in or on the guide tube can be moved axially. Possibly engaged. In another embodiment, the radial projection is arranged at the end of the threaded tube facing the spindle head. The projection engages in an axial guide slot which extends over almost its entire length of the guide tube 1 and is open at one end. In both configurations, the length of the guide tube can be equal to or smaller than the length of the threaded spindle. Each pressure plate has a central hole, the diameter of which is slightly larger than the outer diameter of the guide tube, so that the two pressure plates can be moved on the guide tube. The threaded tube has two diametrically opposed radial fingers, the radial length of the fingers being greater than the radius of the central bore. A recess in the outer surface of the pressure plate remote from the spindle head is also provided at a corresponding diametrical position for accommodating the radial fingers of the threaded tube in a relatively rotationally fixed manner. The two radial widenings of the pressure plate remote from the spindle head, through which the fingers can pass axially, are therefore also arranged diametrically opposite each other. Since both the enlarged part and the recessed part at the edge of the insertion port are arranged in the diametrical direction in this manner, a flat support surface exists on the outer surface of the edge part between them, and the finger is supported on this support surface. In this case, relative rotation cannot be prevented. This creates the risk that the pressure plate will rotate relative to the threaded tube or the radial fingers. This may result in such relative rotation during tensioning of the spring or when handling a tensioned spring that the finger enters the enlargement again and thus releases the pressure plate.

Problem to be Solved by the Invention The object of the invention is to provide a spring spanner of the type mentioned at the outset in a simple form, in which the fingers of the threaded tube are located in a recess in the outer surface of the pressure plate in a relatively fixed manner. The object of the present invention is to ensure that the above-mentioned risk of accidents is reliably eliminated in such a way that a tension connection is possible between the threaded tube and the pressure plate remote from the spindle head only when the spindle head is closed.

Means for Solving the Problems The means of the present invention for solving the above problems are as follows:
In a threaded spanner of the type mentioned at the outset, the threaded tube is provided with at least three approximately wedge-shaped fingers at the end opposite the spindle head, and an equal number of fingers at the end opposite the spindle head. The recesses provided in the outer surface of the pressure plate as well as the radial enlargement of the insertion opening located between each two recesses are such that on the outer surface, at least within the passage range of the fingers, there is a planar support surface for the finger other than the recess. They are all lowered in a sloping manner so that they do not exist.

Effects of the Invention A particular advantage obtained by the invention lies in the elimination of a planar support surface on the outer surface of the pressure plate in the area through which the radial fingers pass, and in the wedge-shaped design of the fingers themselves. It is thus also possible to establish a tensile connection between the threaded tube and the pressure plate only if at the same time a mutually non-rotatable positive connection is formed between the fingers and the pressure plate. Furthermore, finding the recess in the outer surface into which the finger is to be inserted is made considerably easier by the beveled edges of the recess. This also makes handling easier.

Embodiments According to an embodiment of the invention as defined in claim 2, the pressure plate is simultaneously adjusted by the internal dimensions of the insertion opening of the pressure plate remote from the spindle head adapted to the diameter of the threaded tube. The handling is further simplified and convenient in that a radial guidance is established between the threaded tube and the threaded tube, and the centering of the threaded tube in the insertion opening is achieved virtually automatically. Become.

Known spring spanner (West German Patent No. 3304321)
(Specification), the length of the guide tube or bar key alone must be equal to that of the threaded spindle;
And since the pressure plate remote from the spindle head must be movable via the guide tube or bar key in order to achieve the maximum tightening stroke, the insertion opening of the pressure plate is adapted to the outer diameter of the guide tube. If there are two rod-shaped keys, it is necessary to have a corresponding radial enlargement. In one case, it is not possible to adapt the internal dimensions of the insertion opening to the diameter of the threaded tube, since the diameter of the threaded tube is significantly smaller than the diameter of the guide tube. In the other case it would not be possible to implement the configuration of the pressure plate remote from the spindle head according to the features of claim 1. The diagonal guide surfaces provided on both sides of the recess and the enlargement for the passage of the fingers are interrupted by additional passage enlargements for the two bar keys, so that the fingers can move either from the passage enlargement or from the recess. Forced slipping into either will no longer be guaranteed.

This disadvantage is eliminated by the embodiment according to claim 3.

According to the embodiment according to claim 4, a particularly simple anti-rotation element is constructed between the guide tube and the connecting tube or between the connecting tube and the threaded tube. This element also provides good guiding properties between the coupling tube and the guide tube or threaded tube due to its cylindrical shape.

In accordance with the embodiment according to claim 5, it is possible to prevent in a simple manner that the coupling tube is completely removed from the guide tube or of the threaded tube from the coupling tube in the axial direction, or the conventional Handling ensures a permanent bond that cannot be removed. It is easiest to manufacture the anti-rotation member in the manner described in claim 6.

The embodiment according to patent claim 7 is of great importance, since it ensures that the threaded spindle or the engagement of the threaded spindle with the threaded pipe impairs the form-locking coupling connection. This is because it is ensured that the resulting axial tightening forces are not exerted on the anti-rotation web. According to an embodiment according to claim 8, the engagement between the threaded tube and the threaded spindle occurs when the threaded tube is at the maximum axial distance allowed by the coupling tube from the guide tube. is guaranteed to be removed.

According to the embodiment according to claim 9, the maximum tightening stroke is increased to approximately twice the length of the threaded spindle or, with the same maximum tightening stroke, the length of the threaded spindle is reduced by approximately half. It is possible to do this so that the threaded spindle does not protrude from the end face of the threaded tube when the threaded tube is advanced into the guide tube to its maximum extent.

The embodiment according to claim 10 prevents unintentional disengagement of the threaded spindle and the hollow spindle or the hollow spindle and the threaded tube. Claim 1
With the embodiment according to item 1, if necessary, increased forces can be used, for example, to unscrew the threaded spindle completely from the hollow spindle.

In this case, the features of patent claim 7 can also be used to ensure that an axial thrust or tension force is exerted on the anti-rotation webs present in the guide tube and in the coupling tube here as well due to the two couplings. It is advantageous to ensure that this does not occur. This can be achieved by proper length conditions.

The most compact and at the same time lightweight construction of the spring spanner (which is also characterized in particular by a small wall thickness of the guide tube and the connecting tube) also ensures a high relative rotation resistance between the guide tube and the threaded tube. For this purpose, consideration is given to the embodiments according to claim 12 and/or claim 13.
These embodiments at the same time allow easier assembly and disassembly of the spring spanner, which is particularly advantageous in claim 14.
This becomes possible when combined with the features from item 1 to item 18. With the torque overload release clutch provided in accordance with claims 19 to 21, overloads of the threaded spindle can be prevented with sufficient reliability and the risk of accidents is therefore further reduced. .

Embodiment The spring spanner shown in FIGS. 1 to 8 consists essentially of two dish-shaped pressure plates 1, 2, a cylindrical threaded tube 3 and a threaded spindle 4 which can be screwed into the threaded tube 3. and a cylindrical guide tube 5
It is composed of. The threaded spindle 4 is rotatably supported in the guide tube by a thrust bearing 6. The threaded tube 3 has a lower thrust bearing 6
It is equipped with a female thread 7 on the end portion facing the
7), the internal thread extends over approximately 1/4 of the entire length of the threaded tube 3, and the threaded spindle 4 can be screwed into this internal thread. The threaded spindle has at its lower end a flange ring 8 supporting a thrust bearing 6 and a spindle head 9 with a spanner profile projecting axially from the guide tube 5 and an annular groove 10 in the guide tube 5 . An axial movement within the guide tube 5 is ensured by a safety ring 11 arranged therein. The guide tube 5 has a radially projecting annular shoulder-shaped support surface 12 near the spindle head 9, on which the lower spindle head-side pressure plate 2 is supported (more details will be explained later). ).

As can be clearly seen from FIGS. 5 and 7, in this spring spanner the length of the guide tube 5 is approximately 1/2 of the length of the threaded spindle 4. A similarly cylindrical coupling tube 13 is arranged between the cylindrical guide tube 5 and the similarly cylindrical threaded tube 3, and the coupling tube is connected to the guide tube 5.
and a threaded tube 3 to each other in a relatively rotationally fixed manner, so that one tube cannot be rotated relative to the other tube. For this purpose, the coupling tube 13 has on its circumference a flat anti-rotation surface 14 extending over almost its entire length, which prevents rotation from the lower, i.e. guide tube 5.
It ends in an arcuate stop surface 16 at a distance a ₁ from the end surface 15 inserted therein. The guide tube 5 is cut free at its upper end by a transverse cut 17 and has an anti-rotation web 18 which is pressed radially inwardly and lies flat against the anti-rotation surface 14 . Since the anti-rotation web rests positively on the anti-rotation surface 14, it not only prevents relative rotation of the coupling tube 13 within the guide tube;
Since the stopper surface 16 comes into contact with the anti-rotation web 18, it is also possible to prevent the coupling tube 13 from slipping out of the guide tube 5. An anti-rotation element is likewise provided between the connecting tube 13 and the threaded tube 3, i.e. the threaded tube 3 likewise has an anti-rotation surface 14', which prevents rotation. A transverse cut 17' arranged at the upper end of the coupling tube 13 allows the anti-rotation web 18' to be cut free and pressed inwardly into a positive-locking abutment. This anti-rotation surface 14' also extends over almost the entire length of the threaded tube 3 and is located at a distance a ₂ from the lower end surface 15' of the threaded tube 3.
It ends at 6'. The stop surface has an arcuate shape in plan view. In this case as well, the stopper surface 16' comes into contact with the anti-rotation web 18', so that the anti-rotation web 18' allows the threaded tube 3 to connect to the coupling tube 13.
Prevent them from completely escaping.

As can be clearly seen in FIG. 7, the length of the coupling tube 13, more precisely the axial distance l ₃ between the stop surface 16 on the one hand and the anti-rotation web 18' on the other hand, is selected as follows: i.e., for the length of the threaded spindle 4, the threaded spindle 4 reaches the end of the threaded pipe 3 before the stop faces 16 and 16' simultaneously abut against the anti-rotation web 18 or 18' when the threaded pipe 3 runs out. It is adjusted so that it comes off from the screw 7. As a result, the anti-rotation surface 1
It is ensured that 8, 18' are not exposed to axial thrust or tension forces due to the entanglement between threaded spindle 4 and threaded tube 3. To ensure this, the spindle length l ₁ and the maximum stroke movement l ₂ that the coupling tube 13 can carry out in the guide tube 5 must be adjusted;
Anti-rotation web 18' opposite the stopper surface 16
and the distance between _the thread start of the internal thread 7 of the threaded tube 3 and the stop face 16', the following conditions must be met: l ₁ =l ₂ -a ₁ +l ₃ -a ₂ (located in the plane of the stopper surface 16' and the end surface 15' in this example,
The distance between the female thread 7 and the thread start part happens to be a ₂
be equivalent to). It is obvious that the symbol would be different from a ₂ if the thread start of the internal thread 7 was above the stop surface 16'.

As can be seen in FIG. 1, the pressure plate 2, which is supported on the support surface 12 of the guide tube 5 when this spring wrench is used and which is then located near the spindle head, has a central hole 21 as an insertion opening. . The diameter of the central hole is only slightly larger than the outer diameter of the guide tube 5, but smaller than the outer diameter of the support surface 12. Furthermore, the central holes 21 each have widenings 20 arranged at a mutual angular spacing of 120 DEG. At the upper end of the threaded tube 3, i.e. at the end remote from the spindle head, three radial fingers 19 arranged in a star pattern, i.e. also at angular intervals of 120°, can freely pass through the enlargement 20. It is. These fingers 19 are provided to form a relatively non-rotatable tension connection between the pressure plate 1 and the threaded tube 3. For this purpose, the pressure plate 1 also has a central insertion opening 24, which in this embodiment has the basic shape of a cylindrical bore. However, the insertion opening can also have the basic shape of an equilateral triangle, for example with internal dimensions adapted to the diameter of the threaded tube 3. Insertion port 24
is provided with an axially consistent radial widening 22, similar to the central hole 21 of the pressure plate 2, as a passage for the finger 19, the angular spacing between the widenings being 120° and a width and the radial length are each larger than the corresponding dimensions of the finger 19. The outer surface of the pressure plate 1, which can be seen in FIGS. 1 and 2, is provided with an axial recess 23 having a planar support surface 25 in each case centrally between the two widenings 22. As shown in FIGS. The recess 23 is used to receive the fingers 19 of the threaded tube 3 in a positive-fitting manner and thus to form a tension connection between the pressure plate 1 and the threaded tube 3, which cannot rotate relative to each other. In order to eliminate the risk of accidents, it is important to provide means to ensure that the finger 19 is not supported anywhere other than on the support surface 25 of the axial recess 23 in order to form a tension connection. It is. To achieve this,
The edge of the axial recess 23 also has a radial enlargement 22
The edges of the fingers 19 are also sloped in each case on the outer surface, so that conical guide surfaces 26, 27 are obtained that touch or intersect with each other at least in the area of passage of the fingers 19, so that in these areas there is no interference for the fingers. Care is taken so that there is no planar support surface other than the recess 23.

Furthermore, as shown in the side view in FIG. 4, the finger 19 is of approximately wedge-shaped construction, so that the finger 19 has a recess when it is moved from the outside towards the pressure plate 1. 23-1
There are only two possibilities: to slide into the gap or to slide in an axially consistent enlargement.

Furthermore, the two pressure plates 1 and 2 are designed identically in substantially mirror image fashion. Both pressure plates each have the basic shape of a circular plate with a recess 28 in the form of an annular segment extending over approximately 70 DEG to 90 DEG. The notch is used to guide the passage of the spring wire ring. The opposing outer surfaces of both pressure plates are smooth. On the inner surfaces facing each other, a slightly spirally curved annular surface 30 is provided on the inside of an annular collar 29 that goes around the outer edge, and each annular surface is attached to a rubber belt fixed by adhesive or vulcanization. It is provided with a shaped friction lining 31.

The handling and use of such spring spanners is explained in Chapter 9.
A detailed explanation will be given below with reference to FIGS. 10 and 11.

Figure 9 shows the car already removed from the car.
Alternatively, the coil spring 40 is shown before installation, with the spring spanner described above inserted into the coil spring and already ready for tightening. In that case, the insertion is carried out by first inserting the pressure plates 1 and 2 separately in the manner shown from the side between the two races of the coil spring 40 until they assume a position approximately concentric with respect to the spring races. I did this by doing this. Then, from below, the tightening device consisting of the threaded tube 3, the guide tube 5 and the connecting tube 13 of the threaded spindle 4 is inserted axially so that it first passes through the lower pressure plate 2 and then through the upper pressure plate 1. , the three fingers 19 are placed in the recesses 23 of the upper pressure plate. In the state obtained in this way, the threaded spindle 4 can be rotated using a rotary tool with a spanner head 41 that is fitted into the spindle head 9, so that a reduction in the distance between the plates is obtained and this sometimes pressure plates 1 and 2
The spring wire of the coil spring 40 located between the two is compressed. Depending on the number of spring races located between the pressure plates 1 and 2, the spring races can be compressed up to the extent that these races touch. The coil spring 40 is then connected to the lower support plate 42 and the upper support plate 4 of the automobile, for example as shown in FIG.
3 and by suitably rotating the screw spindle 4, the upper pressure plate 1
The wire ring of the coil spring 40 on the outside of the support plate 43
, and both pressure plates 1, 2 can be relaxed until they are no longer exposed to spring pressure. The threaded tube 3 is then moved upwards by further rotation of the threaded spindle 4 until the radial fingers 19 are lifted out of the recess 23 and after rotating the threaded tube 3 by 60° the pressure plate 1 and 2 can be passed through and pulled out downward. The two pressure plates 1 and 2 are then pulled out laterally from the coil spring 40. In FIG. 10, the support plate 42 is inserted into the central opening 42 so that the tightening device, i.e. the guide tube 5, together with the threaded tube 3 can be removed downwardly through the support plate 42.
2'.

In the example of use shown in FIG. 11, the coil spring 40 in a relaxed state extends into a dome 44 inside the vehicle. The wrenches can be removed from the two pressure plates 1 and 2 in the manner described above, and the lower pressure plate 2 can also be pulled out laterally from the coil spring without any problem, whereas the upper pressure plate 1 must be rotated downwards along the annulus until it exits the dome 44 and can be pulled out laterally as well.

In particular, from FIGS. 8 and 10, it can be seen that the distance between the two pressure plates 1 and 2 when the coil spring is tightened is
It can be seen that the lower edge of the insertion port 24 can be contracted until it is supported by the upper end surface 32 of the guide tube 5.

In most vehicle types, in the spring spanner described above, the threaded spindle 4 protrudes from the upper pressure plate 1 by an amount at least approximately equal to the length of the guide tube 5, i.e. equal to 1/2 of the length of the threaded spindle 4. 12 to 15 show a spring spanner with a tensioning device for the two pressure plates 1 and 2, which does not have this disadvantage. In this tightening device, which likewise comprises a guide tube 5, a threaded tube 3 with three fingers 19 and a connecting tube 13, the threaded spindle 4 is arranged such that the threaded tube 3 penetrates into the guide tube 5 to the maximum extent possible. It is only longer than the guide tube 5 by the amount that it protrudes from the guide tube 5 in the axial direction. This operating position is shown in FIG. The guide tube 5 is connected to the threaded tube 3 by means of a connecting tube 13 in a manner similar to the above-mentioned spring spanner shown in FIGS. A hollow spindle 46 is arranged between the threaded tube 3 and the threaded tube 3 . The hollow spindle 46 has an axial length approximately equal to that of the threaded spindle 4 and is provided with an external thread 47 extending over approximately the entire length. The male thread engages with the female thread 7 of the threaded tube 3. The hollow spindle is provided with an internal thread 48 in its lower part, which is connected to the lower end surface 4.
9 for at least five windings in the axial direction. A cylindrical hole 50 having a diameter slightly larger than the outer diameter of the threaded spindle 4 is provided above the female thread 48 .

The part of the threaded tube 3 above the internal thread 7 also has a cylindrical bore 51 whose diameter is slightly larger than the outer diameter of the hollow spindle 46 .

Threaded spindle 4 inserted into cylindrical hole 50
In the end portion of the holder, a twist-out prevention member 52 (for example in the form of a plastic ring or a rubber ring inserted into an annular groove 53) is provided. The role of the twist-off prevention member is to prevent the threaded spindle 4 from twisting downward from the female thread 48 of the hollow spindle 46. Similarly, a twist-out prevention member 54 is attached to the upper end portion of the hollow spindle 46, which prevents the hollow spindle 46 from twisting downwardly out of the threaded tube 3. In both cases, the anti-twisting element 52 or 54 is mounted in such a way that the axial movement of the threaded tube 3 on the hollow spindle 46 or the axial movement of the threaded spindle 4 in the hollow spindle 46 is not hindered. There is.

Threaded spindle 4 by hollow spindle 46
It is possible to make the maximum tightening stroke considerably larger compared to the length of , in particular by the amount by which the threaded tube 3 can be moved on the hollow spindle 46 itself.

Hollow spindle 46 has internal thread 7 of threaded tube 3
To prevent it from twisting upward from the
A retaining ring 56 is disposed in an annular internal groove 55 at the upper end of the threaded tube 3 and a retaining ring 56 is located in the upper end of the threaded tube 3 .
cannot pass through this stop ring.

Due to the arrangement of the hollow spindle 46, the diameters of the guide tube 5, coupling tube 13 and threaded tube 3 are reduced compared to the embodiments of FIGS. 1 to 8 when the diameter of the threaded spindle 4 is equal. 2
It is clear that it must be twice as large.
However, a very important advantage is obtained compared to that, namely that the overall length of the tensioning device or spring spanner of the embodiment of FIGS. on the other hand, the maximum tightening stroke is significantly larger.

Of course, all other advantageous properties of the spring spanner shown in FIGS. 1 to 8 are also obtained in the embodiment of FIGS. 12 to 15.

It likewise comprises a threaded tube 103 with three radial fingers 119, a coupling tube 113, a guide tube 105 with a support surface 112 and a threaded spindle 104 with a spindle head 109 of spanner profile. , Fig. 16, Fig. 17,
In the spring spanner shown in FIG.
5 and the threaded tube 103 is achieved by means different from those in the embodiments described above. Guide tube 105 with sleeve 114 at the lower end
has two diametrically opposed guide slits 115, 116 which are closed at the upper end of the guide tube 105. As best seen in FIGS. 17 and 21, the sleeve 114 ends at an annular shoulder 117 opening into a cylindrical recess 118. The inner diameter of the notch 118 is at least equal to the outer diameter of the guide tube 105 above the sleeve 114. Combined pipe 113
has two guide protrusions 120 and 121 integrally formed at the end on the spindle head side. The guide projections are guided in the guide slots 115, 116 with a slight lateral play and their radial dimensions are at most equal to the wall thickness of the guide tube 105.
Both the guide tube 105 and the coupling tube 113 are perfectly cylindrical, the outer diameter of the coupling tube 113 being relative to the inner diameter of the guide tube 105 such that good telescopic guidance is obtained between these two tubes. It has been adapted. Insertion of the coupling tube 113 into the guide tube 105 is as follows:
This is done by pushing the coupling tube 113 from below into the guide tube 105 through the cylindrical notch 118. In this way, two downwardly open guide slits 1
15 accommodates two guide protrusions 120 and 121. The coupling tube 113 also has two axially extending guide slits 122, 123 diametrically opposed to each other.
have. However, this guide slot is closed at both the upper and lower ends of the coupling tube 113. In order to obtain the most compact and lightweight configuration possible,
Both the wall thickness of the guide tube 105 and the wall thickness of the coupling tube 113 are kept small. The wall thickness is approximately 2-3 mm. On the other hand, there is a female thread on the end part on the spindle head side.
Threaded tube 1 with 07 and subjected to tensile loading
03 has a larger wall thickness of about 5-6 mm. This wall thickness of the threaded tube 103 is such that the guide pin 12
This is sufficient to fix 4,125. The guide pins are press-fitted into coaxial transverse holes 126, 127 in the lower end portion of the threaded tube 103 with an internal thread 107. As the guide pins 124, 125, two spring studs are used which are made by press-fitting the curls of spring steel plates into each other inside and outside. The spring bolts are arranged in guide slits 122, 12 so that they protrude from the circumferential surface of the threaded tube 103 by at most the wall thickness of the coupling tube 113.
3 into the horizontal holes 126, 127, thus connecting the threaded tube 103 and the connecting tube 1.
13 to form a relatively unrotatable connection. The lengths of the guide pins 124 and 125 are set so that the guide pins do not protrude into the female thread 107 of the threaded tube 103 when the guide pins protrude from the peripheral surface of the threaded tube 104 by the wall thickness of the coupling tube 113. selected.
At the same time, this configuration and the selected length of the guide pins 124, 125 ensures that the threaded spindle 103 will not displace when the threaded tube 103 is removed from the coupling tube 113.
When the threaded tube 107 has been twisted out of the threaded tube 107 at least to the extent shown in FIG. 17, the possibility of driving it into the interior through the transverse holes 126, 127 using a suitable punching rod becomes available.

In the embodiment shown in FIGS. 17 and 18, the threaded spindle 104 has an integral flange ring 108, similar to the embodiment shown in FIGS. Bearing 1
Supported by 06. The flange ring is followed by the spanner profile of the spindle head 109. Both the diameter of the flange ring 108 and the diameter of the thrust bearing 106 correspond to the notch 11 of the sleeve 114.
In order to avoid having to choose an internal diameter as large as 8, a cup-shaped cylindrical bearing sleeve 128 is inserted into the recess 118 and supported on its annular shoulder 117. Both the thrust bearing 106 and the flange ring 108 are accommodated in the bearing sleeve and are fixed axially by a safety ring 129. Notch 118 in sleeve 114
A bearing sleeve 128, which is loosely arranged therein and must be easily insertable and removable, is fixed axially in the recess 118 by a safety ring 128.
Two guide slits 115, 11 of guide tube 105
6 is closed by a bearing sleeve 128, and therefore, with the bearing sleeve 128 inserted, the coupling tube 113 cannot be taken out from below.

FIG. 18 shows that in this spring spanner as well, the coupling tube 113 and the threaded tube 103 telescopically intersect with each other and in the guide tube 105, and the inner end surface 131 of the threaded tube 103 is connected to the bearing sleeve 102.
It can be seen that it can be pushed in until it is supported by 8. In this position the radial finger 119
The axial distance from the lower end surface 131 of the threaded tube 103 to the finger 119
approximately equal to the distance. This distance is determined when the guide protrusions 120, 121 abut the upper ends of the guide slits 115, 116 and the guide pins 124, 125 abut the upper ends of the guide slits 122, 123, so that the threaded tube 103 runs to its maximum extent. is approximately equal to one-third of the maximum distance between the support surface 112 and the finger 119 shown in FIG.

Threaded tube 1 shown in FIGS. 17 and 18
In order to prevent excessive rotation of the threaded spindle in the end position relative to the guide tube 105 of 03, and thus damage to the thread threads, it is possible to prevent
0 and 22, the threaded spindle 10 is connected with its spanner profile head 109' via a torque overload release clutch.
4' is taken into consideration. Threaded spindle 104'
comprises a flange ring 108' with a coronal locking tooth 132 on its outwardly facing end face and a cylindrical guiding extension 133 on the outside of this flange ring 108', which is threaded. A dowel pin 134 follows. Spanner profile head 1
09' has a central hole 135 with a diameter adapted to the guide extension 133 and a cylindrical recess 136 of enlarged diameter. The cutout can be closed with a plastic cap 147. Furthermore, the spanner profile head 109'
has a corresponding coronal locking tooth 137 that lockingly engages the coronal locking tooth 132 . Coronal locking tooth 137 is held in engagement by a disc spring pack 138 disposed on threaded pin 134 between nut 139 and an annular shoulder 140 of notch 136. In the embodiment of FIG. 19, the flange ring 108' and thrust bearing 106 have the same diameter as in the embodiments of FIGS. 17 and 18;
and is similarly accommodated within the bearing sleeve 128. However, in order to fix the axial position of the flange ring 108', a spacer bush 141 is required, which is connected to the enlarged diameter extension 142 of the spanner profile head 109'.
are bridged in the axial direction, so that the safety ring 128 can be inserted and removed without problems.

In this embodiment as well, the bearing sleeve 128 is secured to the notch 118 of the sleeve 114 by means of a safety ring 130.
Fixed within.

In the embodiment of FIG. 20, the bearing sleeve 128 is replaced by a bearing plate 143 with a diameter adapted to the recess 118, on which the thrust bearing 106' is supported. A flange ring 108'' is supported on the thrust bearing. Here, both the thrust bearing 106' and the flange ring 108'' are adapted to the inner diameter of the recess 118, but this is not absolutely necessary. The ability to center and guide the threaded spindle 104' in the central bore 145 of the bearing plate 143 by means of the cylindrical extension 144 also results in a thrust guided along the cylindrical extension 144. The bearing 106' and the flange ring 108'' do not require a guide on the inner surface of the recess 118. On the other hand, a spacer bush 146 is also required in this example to fix the axial position of the threaded spindle 104'. Spacer bush 146 has flange ring 108″
and is secured within the notch 118 by a safety ring 130. All other components are considered to be of the same construction as the embodiment of FIG. 19.

By the arrangement of the torque overload release clutch described above (which can be adjusted to various limits by means of a nut 139 and a spring pack 138), the threaded In the two end positions of the tube 103 relative to the guide tube 105, it is ensured that overtwisting of the threaded spindle and thus damage to the mutually engaging threads is avoided. When the spanner profile head 109' is further rotated in either end position of the threaded tube 103, the two coronal locking teeth 132, 137 intermeshing with each other cause the spanner profile head 109' to rotate under the simultaneous axial movement and countersunk. The spanner profile heads 10 are moved apart from each other under the overcoming of the axial spring force of the spring packs 138.
9' relative to the threaded spindle 104'. In order for this overload clutch to be equally effective in both rotational directions, the two crown locking teeth 132, 137 have a symmetrical tooth profile.

Guide tube 105 and threaded tube 10 of the above type
3, the guide tube 10
A high strength is achieved even if the wall thicknesses of both 5 and the coupling tube 113 are small, since in particular the guide projections 115, 116 of the coupling tube 113 can be formed integrally with the coupling tube, i.e. This is because it can be manufactured from real material and of course there is sufficient wall thickness for a stable press fit for the guide pins 124, 125 of the threaded tube 103. The requirements for simple assembly and disassembly are also advantageously met.

For reasons of stability, it is advantageous to arrange the guide projections 120, 121 at an offset of, for example, 90 DEG relative to the guide slots 122, 123 of the coupling tube.

[Brief explanation of the drawing]

1 is an exploded perspective view of a first embodiment of the spring spanner, FIG. 2 is a plan view of the edge region of the insertion opening of the pressure plate remote from the spindle head, and FIG. 3 is shown along the - line in FIG. 4 is a side view of the radial fingers of the threaded tube, FIG. 5 is a sectional view of the spring spanner according to FIG. 1 with the two pressure plates omitted, and FIG. 5 is a sectional view taken along the line - in FIG. 5, and FIG. 7 is a side view, partially in section, of the spring spanner according to FIG. 1 with the threaded tube fully extended, with the two pressure plates omitted. Figures 1 to 7 show the threaded tube fully inserted and the two pressure plates in the tightened position with a minimum axial spacing from each other. Side view of the spring spanner according to the figure,
Fig. 9 is a perspective view of the spring spanner shown in Figs. 1 to 8 used for a coil spring, and Fig. 10 is a cross-section of the spring spanner shown in Figs. 1 to 8 with the spring tightened. Figure 11 is the first
Another example of the use of the spring spanner shown in Figs. 8 to 8 is shown in a state where the compression spring of the automobile is partially protruded into the so-called dome, and Fig. 12 shows a second embodiment of the spring spanner. A perspective view with the two pressure plates omitted; Fig. 13 is a sectional view of the spring spanner shown in Fig. 12 with the threaded pipe partially extended; Fig. 14 shows the spring spanner shown in Fig. 12 with the threaded pipe fully extended. The spring wrench shown in Fig. 12 and Fig. 13 in the
15 is an enlarged sectional view along the line - in FIG. 14, FIG. 16 is a perspective view of the third embodiment of the spring spanner, and FIG. 17 is a slightly enlarged view with two pressure plates omitted. The figure is a vertical cross-sectional view of the spring spanner in the state of maximum length according to Fig. 16, and Fig.
6 and 17, and FIG. 19 shows the part of the spring spanner on the spindle head side with a torque overload release clutch between the spanner profile head and the threaded spindle. 20 is a sectional view of an embodiment in which the spindle head is supported in the sleeve of the guide tube in a manner different from that shown in FIG. 19; FIG. 21 is a view of the sleeve from below; FIG. 22 is a view of FIG. 19; 21 shows the end portion of the threaded spindle of the embodiment according to FIG. 20 on the spindle head side; FIG. 1, 2...Pressure plate, 3,103...Threaded pipe, 4,104,104'...Threaded spindle, 5,
105... Guide tube, 6, 106, 106'... Thrust bearing, 7, 48, 107... Female thread, 8, 10
8,108',108''...Flange ring, 9,1
09... Spindle head, 10... Annular groove, 1
1,130...Safety ring, 12,112...Supporting surface, 13,113...Joining pipe, 14,14'...Rotation prevention surface, 15...End surface, 16,16',25...Stopper surface, 17,17'...Notch , 18, 18'... anti-rotation web, 19, 119... finger, 20,
22...Enlarged part, 21...Central hole, 23...Concave part, 24
...insertion port, 26, 27...guide surface, 28...notch,
29... Annular collar, 30... Annular surface, 31... Friction lining, 32... End surface, 40... Coil spring, 41
...Spanner head, 42...Support plate, 42'...
Central opening, 43...Supporting surface, 44...Dome, 46...Hollow spindle, 47...Male thread, 49...End face, 5
0, 51... Hole, 52, 54... Twisting prevention member, 53... Annular groove, 55... Annular inner groove, 56...
Retaining ring, 109'...Spanner profile head,
114...Sleeve, 115, 116, 122, 1
23... Guide slit, 117, 140... Annular shoulder,
118, 136... Notch, 120, 121... Guide projection, 124, 125... Guide pin, 126, 12
7... Lateral hole, 128... Bearing sleeve, 131... End face, 132, 137... Coronal locking tooth, 133... Guide addition, 134... Threaded pin, 135, 145
...hole, 138...disc spring pack, 139...nut,
141,146...Space subshu, 142,14
4...Additional part, 143...Bearing plate, 147...Plastic cap.

Claims (1)

Claims: 1 Spring spanner for large coil springs, screwed spindle with two loose, disc-shaped pressure plates each with a central insertion opening and a spindle head with a spanner profile. and a cylindrical threaded tube with an internal thread for screwing in a threaded spindle, said threaded spindle being rotatably supported in a cylindrical guide tube by a thrust bearing, and said threaded spindle being rotatably supported in a cylindrical guide tube by means of a thrust bearing. The tube has a radial support surface for supporting the pressure plate on the side of the spindle head, and the threaded tube is axially movable relative to the guide tube by means of a form-fitting guide element. are immovably connected and have a radial finger on the circumference of the end portion opposite the spindle head;
In addition to the radial enlargement forming a passage for the fingers, a recess is provided on the outer surface of the edge region of the insertion opening of the pressure plate remote from the spindle head, into which said finger engages. In those types in which a relatively non-rotatable tensile connection is obtained between the threaded tube and the pressure plate, the threaded tube 3,103 is located at the end opposite the spindle head. at least 3 in
recesses 23 provided in the outer surface of the pressure plate 1 remote from the spindle head with two approximately wedge-shaped fingers 19, 119 and as many recesses 23 as fingers and insertion openings located between each two recesses 23; The radially enlarged portions 22 of the fingers 19 are each lowered in an inclined manner on the outer surface so that at least within the passage range of the fingers 19 there is no planar supporting surface for the fingers other than the recesses 23. and a screw spanner. 2. the fingers are arranged at approximately equal mutual angular spacing around the circumference of the threaded tube 3, 103;
A spring spanner according to claim 1. 3. The insertion opening 24 of the pressure plate 1 on the side opposite to the spindle head side has an inner dimension that is only slightly larger than the outer diameter of the threaded tube 3, 103 and smaller than the diameter of the guide tube 5, 105. A spring spanner according to claim 1 or 2, comprising: 4 Between the guide tubes 5, 105 and the threaded tube 3, both the guide tubes 5, 105 and the threaded tube 3 are connected so that they cannot rotate relative to each other, and are movable in the axial direction relative to both of them. connecting tubes 13, 11
3. The spring spanner according to any one of claims 1 to 3, wherein: 3 is arranged. 5. The connecting tube 13 and the threaded tube 3 each have on their cylindrical circumferential surface at least one flat anti-rotation surface 14, 14' extending substantially over their respective lengths, so as to prevent the connecting tube 13 from rotating. An anti-rotation web 1 of the guide tube 5 protruding radially inwardly on the surface 14
8 in a fitted manner, and the inwardly projecting anti-rotation web 18' of the connecting tube 13 in a fitted manner rests on the anti-rotation surface 14' of the threaded tube 3 in a fitted manner. Spring spanner as mentioned. 6. The anti-rotation surfaces 14, 14' are each provided with a stopper surface 16, 16' at the end of the threaded spindle 4 on the side of the thrust bearing 6, which collides with the anti-rotation webs 18, 18' in contact with each other. Spring spanner according to item 4 or 5. 7. The anti-rotation webs 18, 18' are each formed by a wall section which is cut free and pushed inwards at the end of the guide tube 5 or coupling tube 13 opposite the spindle head. , a spring spanner according to claim 5. 8 Even if the usable thread length of the threaded spindle 4 is maximum, the maximum travel distance l ₂ of the coupling tube 13 within the guide tube 5 and the rotation of the coupling tube with the stopper surface 16 of the rotation prevention surface 14 of the coupling tube 13 Prevention web 18'
It is obtained by subtracting the axial distance a 2 between the stopper surface 16 _' of the anti-rotation surface 14' of the threaded tube 3 and the start of the female thread 7 from the sum of the axial distance l ₃ between Spring spanner according to any one of claims 4 to 7, which is equal to the amount of the spring spanner. 9 A hollow spindle 46 is arranged between the threaded spindle 4 and the threaded tube 3, and the hollow spindle has an internal thread 48 that engages with the threaded spindle 4.
and a male thread 4 that engages with a female thread 7 of the threaded tube 3.
7. A spring spanner according to any one of claims 1 to 7, comprising: 10 Both the internal thread 7 of the threaded tube 3 and the internal thread 48 of the hollow spindle 46 each extend only over a short section at the end on the side of the respective spindle head, and the threaded spindle 4 and/or The spring according to claim 9, comprising untwisting prevention members 52, 56 for preventing the hollow spindle 46 from untwisting out of the threaded tube 3 or the respective internal threads 7, 48 of the hollow spindle 46. spanner. 11. Claim 10, in which the anti-twisting members 52, 56 each consist of an annular member, the annular member being deformable by the respective screw 7, 48 under application of increased force. Spring spanner as described in section. 12 axial guide slot 1 with guide tube 105 closed at the end opposite the spindle head
15, 116, and a guide projection 120, 1 arranged in the guide slit at the end portion of the coupling tube 113 on the spindle head side.
21 is adapted to be guided, and the coupling tube 113 is provided with at least one axial guide slot 122, 123 closed at both ends of the coupling tube, in which the threaded tube 103 is guided.
5. The spring spanner according to claim 4, wherein guide pins 124, 125 fixed to the end portion of the spring spanner on the spindle head side are guided. 13 Guide slit 11 in which guide tube 105 and coupling tube 113 are located diametrically opposite each other.
5, 116; 122, 123, and the coupling tube 113 has two diametrical guide projections 12.
0,121 and threaded tube 103
Spring spanner according to claim 12, characterized in that the spring spanner has two diametrical guide pins (124, 125). 14 Single or multiple guide pins 124, 125
is attached to the threaded tube 103 in a power-conducting but removable manner.
Spring spanner according to item 2 or item 13. 15 The guide pins 124 and 125 each consist of two spring bolts tensioned inside and outside each other, and each of the guide pins 124 and 125 are connected to the threaded tube 103.
15. The spring spanner according to claim 14, which is press-fitted into the horizontal holes 126, 127 of the spring spanner. 16 Guide pins 124 and 125 are threaded tube 10
16. The spring spanner according to claim 14 or 15, wherein the spring spanner is shorter than the inner diameter of 3. 17 Guide slits 115, 11 of guide tube 107
6 is open on the spindle head side, and the thrust bearings 106, 10 of the threaded spindles 104, 104'
Sleeve 114 of guide tube 105 containing 6'
14. A spring spanner according to claim 12 or 13, terminating inside the spring spanner. 18 Two guide slits 11 of guide tube 105
5,116 is closed by an annular shoulder 117 or a bearing ring or bearing plate 143 of the sleeve 114, which is equal to the radial width of the wall thickness of the guide tube 105. Spring spanner according to item 17. 19 The threaded spindle 104' and the spanner profile head 109' with the spanner profile are connected to the torque overload release clutch 13.
Claims 1 to 1 are electrically connected to each other by 2,137,138.
A spring spanner according to any one of items up to item 8. 20 the flange ring 108' of the threaded spindle 104' is provided with a coronal locking tooth 132 on the end face;
A corresponding crown locking tooth 137 of the spanner profile head 109', which is axially displaceably and rotatably mounted on the guiding extension 133 of the threaded spindle 104', is held in engagement with said crown lock tooth. 20. A spring spanner according to claim 19. 21 A compression spring or disk spring pack 138 is inserted in the open cylindrical recess 136 in the end face of the spanner profile head 109' between the nut 139 screwed onto the threaded pin 134 and the annular shoulder 140 of the recess 136. 21. The spring spanner of claim 20, wherein the spring spanner is arranged concentrically about a threaded pin therebetween.