JPH0130598B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a compression device for trash in open-topped containers, in particular cardboard boxes and the like.

Containers of the above-mentioned type are used in particular in wholesalers or department stores for containing waste paper or cardboard and making it possible to remove it.

Traditionally, containers of this type have been filled only by hand, with compression relying on the weight of the cardboard, paper, or other material inside the container. In this case, the disadvantage is that the paper or the like is piled up loosely, so that the storage capacity of the container is not fully utilized and therefore the possible filling volume is not reached.

SUMMARY OF THE INVENTION Therefore, it is an object of the present invention to create a container in which the cardboard, balls, etc. inside the container can accommodate as much waste as possible, especially all kinds of packaging materials generated at the above-mentioned wholesalers and department stores. To provide a compression device capable of easily compressing boxes and the like at a packing place.

To achieve this purpose, the present invention includes:
A driven compression roll is provided that reciprocates over the garbage in the container, and the roll is rotatably supported on the free end of a swinging arm that is pivotally connected to a frame, and the length of the swinging arm is variable. It was configured as follows.

With the above configuration, the roll can be reciprocated over the garbage in the longitudinal direction of the container by its driving means, and in this case, the swinging arm is moved according to the distance between the roll and the swinging arm support of the frame. Can be expanded and contracted.
In this way, the trash in the container is compressed very easily and sequentially, so that the container can contain a much larger amount of trash than with the conventional loose packing method.

The roll may consist of a hollow cylinder closed at both ends, and the material of the roll may be sheet steel. Therefore, if the diameter is approximately 80 cm, the weight will be approximately 200 kg depending on the plate thickness.
It will weigh about 300Kg. It is therefore sufficient for the self-weight of the driven roll to rest on the waste to be compacted. Therefore, it is not necessary to apply an auxiliary compressive force to the rolls.

It is particularly advantageous if the roll drive means are internal to the roll, since the weight of the roll is thus further increased by the drive motor and the associated transmission mechanism. In this case, it is preferable that the drive means has a spur gear transmission mechanism. The spur gear transmission mechanism is arranged together with the drive motor in the middle of the roll, which is fixed to the free end of the swinging arm. Two rotatably supported outer roll hollow parts connect to the intermediate part.

In this case, the drive motor is arranged eccentrically with respect to a through shaft actuated by a spur gear transmission, with the drive motor projecting into one of the two hollow parts parallel to said shaft. It is preferable to do so.

Experiments have shown that for a diameter of about 80 cm, it is preferable to design the roll drive means such that the roll travels about 25 revolutions per minute. The intermediate fixed part of the roll consists of the housing of the transmission mechanism or the cover of its housing, which can at the same time form the bearing of the two rotating hollow parts of the roll or of its shaft.

Preferably, the length of the rocker arm is varied by constructing the rocker arm from individual parts that can be inserted into one another in a telescoping manner. In this way, by inserting the nested parts into each other, the distance between the axis of the roll and the upper bearing of the rocker arm is changed during horizontal movement over the waste to be compacted, and the rocker arm When passing by the side of the pedestal supporting the swinging arm,
Take the minimum length.

Further, it is advantageous if the pedestal supporting the swinging arm is provided with a hydraulic lifting mechanism, and the fulcrum at the upper end of the swinging arm can be moved up and down by the lifting mechanism. This makes it possible to level out the height of the deposit inside the container by shifting the fulcrum of the swinging arm upwards to varying degrees depending on the amount of dirt already in the container.

To ensure that the driven roll does not collide with the container wall, the length of the swinging arm from its upper fulcrum to its lower free end plus half the roll diameter must be less than half the length of the container. Preferably it is slightly shorter. In this way, there is no risk of the rolls colliding with the walls of the container, even if the swinging arm makes very sharp angles with the horizontal in each extreme position.

Other configurations are also possible in which the lateral movement of the roll is limited by a limit switch or the like and the direction of rotation is automatically switched at each extreme position.

Furthermore, the hydraulic lifting mechanism of the frame of the apparatus of the present invention is also used for loading and unloading rolls into and from containers. For this purpose, a swinging arm portion is provided that protrudes beyond the fulcrum of the frame to the opposite side of the roll, and at the position where the swinging arm is rotated, the end of the swinging arm on the side away from the fulcrum is secured by a connecting rod, chain, etc. It can be pivoted to a pedestal. With this pivoting, the swinging arm can be rotated upwardly from the container by raising the fulcrum, and conversely, the swinging arm can be rapidly lowered into the container by lowering the fulcrum. Therefore, when the swinging arm is rotated, the stroke of the hydraulic mechanism is expanded with various leverages based on the length of the swinging arm.

In the case of the telescoping arrangement of the rocking arms as described above, it is particularly preferred that the last part of the telescoping hollow body forms an arm projecting beyond the fulcrum, on which the connecting rod or chain acts.

It is of course possible to arrange the stand on the end face side of the container, but it is also possible to place the stand in the center of the container, the arm extending above the container, and the fulcrum of the swinging arm being placed at the free end of the arm. It is particularly preferable. In order to secure and secure the pedestal during the compression movement, the pedestal is provided with a large base plate, which extends below the container;
Preferably, the container rests on it. In this way, the stand is securely held by the weight of the container. Additional connecting means between the substrate and the container can be provided, such as mutually engaging notches.

Particularly for this purpose, the base plate is provided on its end side with a stop rail which extends from below above the relevant end face of the container, against which the container rests by an obliquely downward sliding movement and is in use. The substrate can be configured to be in contact with this. In this way, the substrate, the pedestal and the container are arranged relative to each other so that the pedestal is always in the center of the container.
The container can be removed from the substrate configured in this way in the opposite direction by a diagonally upward upward movement. In this case, it is preferable that the rollers be located on the side facing away from a crane or other container removal device so that the rolls do not collide with a wall surface during container removal.

Preferably, the drive motor of the roll is configured as a reversing motor, such that by switching in the extreme position the roll moves in reverse over the garbage. This switching can be controlled manually or by limit switches operating at each extreme position. If the swinging arm performs the same deflection movement in each case, the limit switch can be actuated by the swinging arm or by a stop arranged on the swinging arm. This presupposes that for each successive reciprocating movement of the swinging arm, the upward movement of the frame each time raises the fulcrum of the swinging arm by a certain distance.

Particularly preferably, the above-mentioned raising is carried out in such a way that, upon retraction of the rocker arm, the rocker arm collides with a stop and the piston rod supporting the fulcrum of the rocker arm moves upwards in the floating position of the hydraulic mechanism. be able to. If a check valve is inserted and the check valve holds the pressure hydraulic fluid forced toward the piston rod in the thus induced position, the piston or piston rod of the hydraulic mechanism will remain in this position. , the fulcrum of the swinging arm automatically moves upward. However, this does not prevent compaction of the debris within the container. because,
This is because the roll can continue to freely compress the garbage in the container due to its own weight.

In that case, the check valve can be used to lower the raised hydraulic mechanism again when it is inserted into a container to be newly filled.

Thus, for the actual operation during the compression process, only one operating button is required on the operating wire or the like attached to the fixed cross beam. When the actuating button connects the drive means of the roll, the roll is automatically reciprocated over the garbage by means of the limit switch in the two extreme positions, the fulcrum of the swinging arm being adjusted according to the filling height reached. automatically lifted.

The hydraulic mechanism can also be operated externally. However, this is actually only necessary when changing containers. Therefore, the person who performs this operation is not the person who fills the container, but the person who delivers the container and comes to pick it up.

To ensure that the roll can move over a relatively smooth material for compaction, the roll surface is roughened or has projections etc. that are transverse to the direction of roll movement and thus extend along the roll. It is preferable to have the following. The protrusions may be flat bars or the like that terminate about 15 mm above the roll surface so as not to penetrate too deeply into the material to be compressed and tear it unduly.

In order to guarantee the power supply to the rolls, it is suitable to arrange a cable reel at the upper free end of the telescopically retractable swinging arm, such as those used in construction machines, etc., where the cable must be constantly extended and retracted. be.

In addition, at least one in each end area of the roll is provided, in order to prevent the material from being pressed too tightly in the wall area of the container, creating a prestress and thus making it difficult to empty the container later. Preferably, a rim is provided, which rim annularly surrounds the roll, the upper edge of the rim being above the roll surface. The rim is thus pressed into the material in the vicinity of the wall area of the container, thereby effectively limiting the pressing area of the rolls, so that in the immediate area of the container wall there is no possibility of over-tightening of the material by the inner wall surface. This will not occur. Preferably, both end-side ends of the roll are provided with outwardly curved walls or covers in order to avoid damage from impact with walls in the event of lateral forces. Even if the roll hits a wall of the container, the outwardly curved wall or cover recenters the roll.

The above-described configuration requires a certain amount of manufacturing and space costs and is therefore particularly suitable for large containers.

The swing arm is provided with at least one pin joint dividing the swing arm, and at least one stop is provided in the area of the pin joint to prevent full extension of the swing arm and to prevent the swing arm from fully extending. An arrangement in which the two connecting rocker arm sections sandwich an angle of less than 180 DEG in the extended position of the roll is especially economical to use for small containers.

With this configuration, during the reciprocating movement of the roll above the compacted waste, the swinging arm portion connected by the pin joint is bent, so that the overhang length of the swinging arm can thus be changed very easily and the roll can move on the garbage in the container.

one portion of the pin joint is configured as a fork;
A particularly simple construction of the pin joint is obtained if the other joint part engages between them and a pin passing through both parts connects these parts. In this embodiment, it is particularly preferred that the stop consists of a further pin which is external to the coupling pin and passes through the outer fork. In such a configuration, since the bifurcated joint portion touches the stop pin at the end of the extension movement of the swinging arm, further extension movement is thereby prevented and an angle smaller than 180° is maintained. It will be done. This corner allows the swinging arm to subsequently deflect during the roll's backward movement.

A rocker arm of the type described above can also be used in the configuration described above, in which the rocker arm passes in pendulum fashion with a progressively shorter length past a pedestal installed in the center of the container. However, such a configuration ensures that even if the apex of the corner between the parts of the swinging arm reaches the lower part during the movement of the swinging arm, the joint area of the said part will not plunge into the garbage, and the joint will remain intact. The fulcrum of the swinging arm is mounted above the last dirt layer in the container or above the top edge of the container by at least the length of the swinging arm so that it passes over the trash. shall be. This is a relatively high platform and
This results in a large and heavy structure.

It is therefore particularly advantageous if the rocker arm is movable only on one side of the pedestal, and in this range of motion the apex of the corner formed between the rocker arm parts is at the top.

In this way, the pin joint can only move upward during the bending process. Collisions with dirt or the bottom of the container can therefore not occur. At the same time, the fulcrum of the swinging arm only needs to be directly above the top layer of trash or the edge of the container.

Is the width of the roll smaller than the width of the waste passing through?
In this case, it is particularly preferable to arrange the stand on the long side of the container. This is because in this case, the width of the roll only needs to be smaller than or approximately equal to the inner width of the container. Since the roll itself is thus relatively narrow, it can be manufactured at low cost. However, in that case, the container must travel a longer path than when the platform is on the short side of the container.
However, the specific plane pressure force that the roll applies to the garbage is
The narrower, much cheaper rolls are just as good as the other configurations.

A particularly advantageous configuration results if the swinging arm is divided into three parts with two pin joints between them.

Since this configuration results in relatively small deflections of the individual parts and upward movements of the pin joints, the overall The height doesn't get too big.

In this case, the first swinging arm portion connected to the fulcrum of the frame for loading and unloading the roll stands almost vertically,
It is particularly advantageous if a second part is connected at right angles to this part and furthermore a third part with a roll having a drive inside it suspends downwardly at right angles to the end of the second part. be. In that case, in order to maintain a right angle between the first and second parts, it overhangs the second part in a position at right angles to the first part, and the second part rests in this position. Preferably, a support is provided in the area of the pin joint.

In order to place the swinging arm in the above-mentioned position for loading and unloading the roll, a lifting mechanism arranged under the fulcrum of the frame moves the first part connected to the fulcrum into the vertical position via a semicircular roller. An action can be applied to the end of a towing rope, etc. With said semicircular roller, in all pivoting positions of the first part,
It is ensured that the force acts on the first part with the same leverage.

Preferably, the lifting mechanism for vertically aligning the first part of the rocking arm consists of a rack-type winch, the housing of which is pivotally connected to the pedestal in its lower region. The upward free end of the rack can be connected to a traction rope guided through semicircular rollers. The rack is actuated by a hand crank via a gear rotatably disposed within the housing. The end of the towing rope facing away from the rack winch is fixed to the semicircular roller itself or to the erected first part of the swinging arm in the section of the semicircular roller facing away from the rack winch.

The semicircular roller itself is fixed to the first part of the rocker arm and is moved therewith.

In this way, during the pivoting movement of the first part of the swinging arm, no relative displacement occurs between the traction rope and the semicircular roller, and the traction rope only partially rests on or away from the semicircular roller. to be released.

In order to adapt the compression device according to the invention to different overall container heights, the height of the pedestal is preferably variable. A simple and rigid construction can be achieved if the pedestal itself consists of two parts that are mutually movable longitudinally, each part preferably nesting in one another and can be fixed in various relative positions. to be born.

If telescoping sections are used, fixing can be easily achieved by aligning the recesses of both sections and inserting a transverse locking pin there.

In this configuration example, for such height adjustment,
In particular, this provides an advantageous possibility of using the lifting mechanism, which is designed as a rack type winch, for lifting and lowering the upper movable part of the platform. For this purpose, the upper movable part of the frame is provided with a universal joint, to which the upper end of the rack can be optionally connected. This universal joint consists of a simple joint pin inserted through a connecting plate or the like fixed on the upper end of the rack on the one hand and on the upper movable part of the frame on the other hand.

To connect the top of the rack and the top of the pedestal,
The tow rope must be removed from the rack.
For this reason, the connection to the rack end preferably consists of a shackle. At the same time, when the first part of the swinging arm and the top of the pedestal are aligned vertically,
A locking is provided between the two parts to prevent the swing arm from bending when the tow rope is removed. This locking can consist of a pivotable stop bar or the like. The stop bar is supported on the upper part of the pedestal and engages in a slit or the like in a vertical position of the first part of the swing arm.

However, the above-mentioned locking is only necessary if, for special reasons, the height adjustment is or must be carried out with the first part of the swinging arm in the upright position. This is because in this case, the weight of the roll acting on the frame via the lever arm of the second part must also be moved at the same time.

Therefore, it is advantageous to adjust the height of the stand while the roll is placed in the container or elsewhere. By placing the roll and supporting it, the tow rope can be released without securing the swinging arm. In that case, when adjusting the height, it is only necessary to shift part of the weight of the top of the pedestal or the swinging arm.

In addition, individual locking holes or Rope hooks are arranged on the first part of the swinging arm at intervals corresponding to the vertical interval of the hollow part, and the upper end of the towing rope is hooked on the hook according to the height adjustment. . In this way, the housing of the rack type winch can remain fixed to the lower part of the pedestal when the height of the upper part of the pedestal is varied.

In this configuration, too, automatic switching is used in order to automatically advance the compaction of the waste and to prevent the rolls from colliding with the walls of the container. For this purpose, at least two limit switches are provided for each reverse switch, which can be actuated via cams that are displaced by an operating cable. In that case, one end of the operating cable is fixed to one of the parts of the rocker arm, and the other end acts on a cam that is guided to be movable along another part of the rocker arm or the pedestal. Further, the operating cable is guided to the outside through the pin joint.

In this way, the actuating cable is pulled during the bending movement, so that the movably constructed cam is moved correspondingly. Thus, when fully deflected, the cam is moved to one extreme position relative to one limit switch, which reverses the direction of rotation, but when the rocker arm is extended, the other limit switch is actuated as well.

In this case, it is preferable that the traction rope is a flat strip. This is because such a strip can be guided with particularly low wear by fixing pins or the like.
In this case, the flat strip preferably consists of a wear-resistant plastic.

Preferably, a return spring acting on the cam is provided to ensure a backward movement during the extension movement of the swinging arm.

The first swinging arm is used to operate the limit switch.
It is also possible, at least in combination, to use a bending movement between the part and the pedestal, so that the limit switch is arranged in the pedestal and the end of the traction rope in one part of the swinging arm. , it is preferable to utilize a pin joint between the parts of the rocker arm for the operation of the limit switch, so that the guide of the cam is arranged in the first part of the rocker arm. As mentioned above, if the rocker arm consists of three parts, the other end of the operating cable can be connected to the first part of the rocker arm in order to obtain the largest possible stroke of the cam, using the deflection movement of the two pin joints. 3
It is preferable to fix it to the part.

It is particularly advantageous if the operating cable is guided by a stop pin of a pin joint. This is because, in the bent state, this stop pin is at a considerable distance outside the articulation point, that is to say outside the outer wall surface of the individual member of the rocker arm. In order to convert the tension caused in this way in the cable into a cam stroke as large as possible, the cable is passed in the vicinity of each pin joint under a guide pin fixed to the trailing part of the swinging arm, which is preferably held near the wall of the swinging arm. Thus, over most of the length of the rocker arm in question, the actuating cable is guided approximately parallel to each part of the rocker arm and is pulled away from the pin joint by means of the stop pin only in the region of the pin joint.

Preferably, the cam is mounted on a guide rod movably arranged on a fixed bearing. In that case, an actuating cable acts on one end of the guide rod and a return spring, which is designed as a tension spring, acts on the other end of the guide rod. In this way, each bending movement of the swinging arm causes the guide rod to be reciprocated in the bearing by means of the operating cable.

The configuration of the cam and the operating cable according to the invention makes it possible, in particular, to adjust the deflection movement of the swinging arm to containers of different sizes. This means that
This is done by adjusting the cam on the guide rod and fixing it in the extreme position concerned. This fixation is achieved, for example, by the guide rod engaging a hole in the cam and by fixing the cam to the guide rod with a set screw. Therefore, depending on the adjustment position of the cam on the guide rod,
The swinging arm performs deflection movements of various magnitudes. In that case, it is also possible to extend this movement to one side, so that, for example, the container can be placed in such a way that it can be removed from the pedestal, or a roll force is applied only to part of the contents of the container. can.

Preferably, limit switches are arranged at opposite ends of the switchbox in the area of the path of movement of the cam. The switchbox can then be fixed between the bearings of the guide rod of the first part of the rocker arm.

A particularly simple construction is obtained if the cable operating mechanism described above is replaced by a hydraulic device. For this purpose, a hydraulic system is arranged in the area of the fulcrum of the pedestal, so that one end of the hydraulic system is pivoted to the pedestal inside each bend, and the other end is supported on the pedestal. Preferably, the swing arm and the part of the pedestal, each extending from the fulcrum to the point of action of the hydraulic mechanism, form a triangle together with the hydraulic mechanism.
The protrusion of the hydraulic mechanism therefore results in the raising of the rocker arm, and vice versa.

If a hydraulic mechanism is used, it is sufficient for the rocking arm to consist of two parts. The part that carries the rolls is linear, and the part that connects to the frame consists of two linear pieces that are rigidly connected to each other at their corners. In this lowered state of the roll, the pieces of the rocking arm on the side away from the fulcrum are generally horizontal, so that the entire arrangement occupies a relatively small space in use. In addition, the weight distribution during lifting and lowering of the rolls is relatively good. In this case, the angle between the two pieces is preferably about 135°. In addition, in order to reduce the cantilever load and reduce the size of the hydraulic mechanism, the platform also consists of two linear pieces that are rigidly connected to each other, the lower piece of which stands upright and has a rocking arm. A second piece having a fulcrum is angularly connected to the lower piece and directed outwardly away from the roll, the angle between the two pieces being approximately 150°. It is preferable.

Further, the first piece of the first part of the swinging arm connected to the part carrying the roll has a bearing for the push rod parallel to the piece, and the side closer to the piece connected to the fulcrum has a bearing for the push rod parallel to the piece. the push rod end protrudes beyond the first piece;
By providing two adjustable cams for operating the limit switch, the limit switch for reversing the roll rotation direction can be easily operated. In this case, the limit switch is preferably located on a support provided on the individual piece.

For actuation of the push rod, it is preferred that the straight part of the rocker arm is provided in the area of the pin joint with an extension that projects beyond the pin joint. An intermediate rod is pivoted at the end of the extension, the other end of which acts on the corresponding end of the push rod.

Next, the present invention will be explained in detail based on embodiments shown in the drawings.

According to FIG. 1, a compression roll 4 is provided in a container 1, which can reciprocate in the direction of an arrow 3 over the garbage 2 therein, and a swinging arm 5, which is pivoted on a pedestal 6, is free. It is rotatably placed at the end. The compression roll 4 is driven to reciprocate in the direction of the arrow 7 in order to move on the garbage 2 in the direction of the arrow 3.

The rocker arm 5 is pivoted at the upper end of the frame 6 at reference numeral 8 and consists of a plurality of individual parts 9 inserted into one another in a telescoping manner.

The pedestal 6 is equipped with a hydraulic lifting mechanism 100. This elevating mechanism 100 moves the fulcrum 8 up and down in the direction of an arrow 110.

The drive means for the roll 4 are within the roll itself (see Figure 3). Drive motor 1 installed there
A cable reel 130 is arranged at the upper free end of the swinging arm 5 for supplying current to the swing arm 5 .

The surface of the roll 4 is provided with projections 140 transverse to the direction of movement of the roll. The projections 140 therefore extend in the longitudinal direction of the roll 4. This protrusion is intended to ensure movement of the roll on relatively smooth materials.

The pedestal 6 includes a substrate 150. The substrate 150 overhangs the container 1 and therefore rests on it. This substrate 150 is provided with a stop rail 150a extending from below on the end surface side of the container. As shown, the container rests against this stop rail 150a in use. The substrate 150 is directly connected to the base plate 16 of the frame 6.

The plan view in FIG. 2 makes the above situation clear. It is also clear in FIG. 2 that the hydraulic lifting mechanism 100 has at its upper end an arm 170 that overhangs the container, at the end of which there is a support 8 for the swinging arm 5. In addition, as shown in the figure, the stand 6 is connected to the container 1.
It is arranged in the center of the vertical extension of.

In the illustrated embodiment, the sum of the length L of the swinging arm 5 in the pulled out state and half the roll diameter D is the length A of the container.
Since it is selected to be slightly smaller than half of , there is no risk of the roll colliding with the container wall even when the swinging arm 5 is in a horizontal position.

The drive motor for the roll 4 is of a reverse-acting type, and its direction of rotation is reversed by a limit switch (not shown). Also, when the swinging arm 5 passes by the platform 6 in a fully retracted state, the swinging arm collides with the stop, and thus the piston rod or arm 170 or the hydraulic mechanism part supporting the swinging arm fulcrum 8. The hydraulic mechanism 100 is designed in such a way that the filling level is pushed upwards by the amount of filling reached at that time. In this position, the hydraulic fluid is displaced and stopped by the non-return valve as described above, so that the part of the hydraulic mechanism supporting the fulcrum 8 cannot again descend downwards when the rocking arm continues to move. I can't.
In this way, the fulcrum 8 is automatically raised depending on the filling state.

Portion 90a carrying cable reel 130 so that roll 4 can be easily loaded and unloaded
protrudes beyond the fulcrum 8 to the opposite side of the roll 4. The end of this part on the back side of the fulcrum 8 is connected to the connecting rod 18
0 is pivotally connected to the frame 6 at reference number 190 via a chain or the like, and the connecting rod or the like is connected to section 9 at reference number 200.
It is pivoted to 0a and acts on it. If the hydraulic mechanism 100 now moves upwards, since the length of the connecting rod 180 is constant, the roll 4 will undergo a large pivoting movement in the direction of the arrow 210, and will thus be easily removed from the container. Alternatively, if the hydraulic mechanism 100 moves downward, it will be inserted into the container.

The function of the above arrangement is thus as follows.

When installing the container 1 on the substrate 150 (this is done in the direction of the arrow 220), the hydraulic mechanism 100
is in a raised state, and the roll 4 is rotated upward. That is, the roll 4 takes approximately the position indicated by the broken line in FIG. When the container 1 is placed on the base plate 150 and abuts against the stop rail 150a, the hydraulic mechanism 100 is lowered, and then the roll 4 moves downward until it reaches the bottom of the container.

Here, garbage is packed and the driving means for the roll 4 is connected. The rolls then move back and forth over the trash 2 in the direction of the arrow 3, the direction of rotation of the rolls being reversed in each case by means of a limit switch. The limit switch is activated when a predetermined angle α between the longitudinal axis of the swinging arm 5 and the vertical is reached. At the same time, the respective extreme positions in the vicinity of the end wall of the container 1 are also determined. When the roll 4 passes by the pedestal 6, i.e. when the swing arm 5 is compressed significantly, the swing arm 5 impinges in each case on a stop, which stops supports the fulcrum 8 of the swing arm 100. Push up the part. As previously mentioned, a check valve is provided to hold the hydraulic mechanism in the position it assumes. In this way, the fulcrum 8 is automatically raised depending on the relevant filling quantity. A check valve can also be used at the same time to lower the hydraulic mechanism.

Next, when the filled container is to be removed, the hydraulic mechanism 100 is raised again and the roll 4 is unwound from the container 1. If this is done,
The container can be removed diagonally upwards in the direction of arrow 220.

FIG. 3 shows the structure of the roll 4 of the device according to FIGS. 1 and 2 in a cross-sectional view. According to Figure 3,
The roll 4 comprises an intermediate part 230 fixed to the lower part 9 of the rocker arm 5. The intermediate portion 230 is used as a cover for the spur gear transmission mechanism 240. Spur gear transmission 240 is driven by drive motor 120 and itself drives shaft 250 . The bilaterally oriented shaft 250 carries two hollow portions 260 and 270 at each end. Therefore, these hollow portions are rotated by the drive of the motor 120. These hollow portions 260, 270 are provided with projections 140 on their surfaces or are suitably roughened. The hollow portions 260 and 270 can freely move relative to the intermediate portion 230 via a labyrinth guide 280 or the like.

A rim 290 is arranged in the area of the end faces of the two parts 260 and 270 of the roll 4;
It encircles the part of the roll in an annular manner and its upper edge is above the roll surface. As previously mentioned, this rim is intended to prevent the material from being overly tightened by the inner surface of the container wall. In order to avoid damage to the container 1 which is not yet filled with garbage, this rim can be provided with a covering in the form of a rubber tire.

In the embodiment according to FIGS. 4 to 10, the rocker arm 5 is pivoted at the upper end of the frame 6 at reference numeral 8 according to FIG. It consists of members 9a to 9c. A stop 11 is provided in each case in the area of the pin joint 10 to prevent the swing arm 5 from fully extending, so that the two parts of the swing arm 5, each connected to the pin joint 10, can be rotated as shown in FIG. At the protruding position of 4, pinch an angle smaller than 180°.

In this case, a part of the pin joint 10 is bifurcated 10a
(see FIG. 6) between which a further joint part engages, the joint being connected by a pin 12 (see FIG. 6) passing through the two parts. The pin 12 has a chamfered portion attached to a flat retaining plate 13.
is non-rotatably connected to the forked portion by abutting the forked portion.

As can be seen in FIGS. 4 and 6, in the illustrated embodiment the stop 11 also consists of a pin, which is located outside the coupling pin 12 and also passes through the fork 10a.

In this embodiment too, the pedestal 6 has a large base or platform 16 on which the container 1 rests. In the embodiment shown, the platform 6 is located on the long side of the container 1, and the swing arm 5
can only be moved on one side of the platform 6. In that case, as shown, the individual members 9a to 9c
The vertex 14 of the angle α between them is on the upper side. During the movement of the roll 4, the rocker arm 5 is therefore bent upwards into the position shown in broken lines, so that the apex 14 also moves upwards and is not guided downwards towards the wall of the container or the garbage. At the same time, the fulcrum 8 of the swinging arm only needs to be directly above the edge 15 of the container 1.

For loading and unloading the swinging arm, a lifting mechanism in the form of a rack winch 18 is arranged in the lower part 17 of the frame 6, which is fixed to the base plate or base 16. The rack winch 18 acts on a second member 9a of the swinging arm 5, which is connected to the fulcrum 8, via a traction rope 19 which is fixed via a semicircular roller 20 to a rope hook 21. As shown, a rope hook 21 is provided for height adjustment, which will be described again later.

The movable part 22 engages in the fixed part 17 of the frame 6 in a telescoping manner. The movable part 22 can be connected to the fixed part 17 at different heights. For this purpose, both parts can be provided with a through hole 23 or the like,
A locking pin can be inserted into it. To move the movable part 22 upward or downward,
A connecting plate 24 is provided on the movable part 22, which extends above the lower part 17 in the retracted state, and after removing the tow rope 19, said connecting plate 24 is inserted at reference numeral 25 into the rack 26 of the rack winch 18. It can be connected to the top end.

FIG. 5 shows the device of FIG. 4 in an upright position. In this state, the first member 9a of the swinging arm 5 is aligned with the platform 6. For this purpose, the towing rope 19 guided through the semicircular roller 20 is moved by a hand crank 28 by means of a rack winch 18 at the arrow 2
7 until the alignment according to FIG. 5 is obtained.
Towed. The device can be fixed in the position shown in FIG. 5 by means of a locking 29 which engages in a slit or the like in the vertical member 9a.

In the position shown in FIG. 5, the roll 4 can be inserted into or removed from the container 1, which is indicated by dashed lines in FIG.

In order to adjust the device to different container heights, the tow rope 19, which is secured to the rack 26 by means of a shackle 30, is removed from the rack 26 and the rack is then placed in the position shown in broken lines in FIG. The movable portion 22 of the frame 6 is adjusted by connecting it to the connecting plate 24 at the reference numeral 25 by means of a joint pin or the like provided there. As mentioned above, the moving part 2
The lower area of the articulation plate 24 has a spacing A with respect to the movable part 22, such that the articulation plate 24 overhangs the fixed part 17 when the part 2 is inserted telescopically into the fixed part 17. Therefore, the movable part 22 can be moved up and down by the winch 18 and can be locked by the hole 23 at each desired position.

In the embodiment shown in FIG. 5, the intermediate member 9b is held by supports 31 in a position at right angles to the first part 9a. The support 31 overhangs the second member 9b, on which the second member 9b rests, when the second member 9b is in a position perpendicular to the first member 9a. In that case, the third member 9c hangs vertically due to the weight of the roll 4 and the drive means therein. If the tow rope 19 is hooked, there is no risk of the device falling over even if it is not locked. This is because the roll 4 keeps the first member 9a vertical at all times via the lever formed by the second member 9b.

In the case of the above-mentioned height adjustment, the tow rope 19 is
Hang the upper end of the rope hook 21 on the rope hook 21.

FIG. 6 is a front view taken along the lines of FIG. 5, and shows in particular the construction of the two-part connecting plate 24 on either side of the semicircular roller 20. FIG. In this way, the pin can be inserted into both parts along the axis 25, and the upper end of the rack 26 can be engaged between the parts.

The roll 4 has a width B as shown. In order to avoid that the compacted waste is pressed too strongly against the inner surface of the container, B mentioned above is considerably smaller than the internal width B ₁ of the container 1 indicated by the dashed line.

Also, as is clear from Figures 4 to 6,
In the position according to FIG. 6, the stop pin 11 is above the joint pin 12 in the area of the dorsal edge of the second part 9b of the first part 9a, so that according to FIG. In the cut state, the stop pin 11 is on the upper side of the trailing member 9b, while the trailing member 9b abuts against the pin 11.

7 and 8 show an embodiment of the fulcrum 8. FIG.
The fulcrum 8 is a fork 3 fixed to the movable upper part of the pedestal 22.
Consists of 2. A pin 33 is passed through the fork 32, and the pin 33 is provided with a chamfered portion 34, thereby being non-rotatably connected to the fork 32 via a flat plate 35. The pin 33 passes through a bushing 36 fixed to the first member 9a of the connecting swing arm 5 and is secured by a pin 37 on the opposite side.

Furthermore, FIGS. 5 and 6 also show an automatic switching mechanism for a reverse drive motor disposed inside the roll 4. This mechanism consists of an operating cable 38 in the form of a flat plastic strip, which in the area of the pin joint 10 is guided via a stop pin 11 which projects in a bent position.
One end 38a thereof is fixed to a third member 9c, while the other end 38b is a guide rod 39 carrying a cam 40.
It acts on 2 limit switches 41, 42
is operated by the cam 40 mentioned above. The limit switches 41 and 42 are disposed on a switchbox 43, and the switchbox 43 is connected to the swinging arm 5.
is held by the first member 9a.

In the area of the pin joint 10 the operating cable 38 is attached to the supporting arm or the like and is attached to the trailing members 9b and 9 of the swinging arm.
It is passed under a guide pin 44 fixed to b.
The guide pin 44 thus holds the operating cable 38 between it and the following pin joint close to the wall of the rocker arm or part in question.

Figures 9 and 10 show enlarged details of this switching mechanism. As is clear in FIG.
1,42 are carried on both ends. In this case, supporting arm 4
5 is located between two plain bearings 46 of the guide rod 39. The plain bearing 46 is also connected to the first member 9 of the rocking arm.
It is fixed at a.

A cam 40 is arranged on the guide rod 39 between two bearings 46 . In this case, the cam 40 is provided with a hole through which the guide rod 39 passes. Guide rod 39
In this adjusted position, the cam 40 can be fixed by means of a schematically illustrated set screw 47 or the like.

A tension spring 48 acts on the lower end of the guide rod 39 in FIG. The other end of the tension spring 48 is fixed to the member 9a in the area of the fulcrum 8 between the frame and the first member 9a. A tension spring 48 is used for the return of the guide rod, the length of which allows an elastic stroke as large as possible.

The operation of the embodiment according to FIGS. 4 to 10 is as follows.

Each member 9a to 9 according to FIGS. 2 and 6
When the extending motion of the swinging arm starts from the relative position of c,
That is, when the swinging arm begins to approach the position shown in FIG. 4, the deflection of the operating cable in the area of the stop pin 11 becomes smaller, so that the guide rod 39 moves toward the fulcrum 8 in the direction of the arrow 49. At the same time, the upper cam 40
leaves limit switch 41. This movement continues until the lower cam 40 reaches the lower limit switch 42. In this position, the maximum extension specified by the position of the cam on the guide rod is reached and the direction of rotation of the roll is reversed, so that the bending process begins anew and eventually the upper cam 47 reaches the limit switch 41. do. A new stretching movement is then started.

FIG. 11 uses a bendable swinging arm and a hydraulic mechanism 50 for loading and unloading the roll. Another example is shown. The hydraulic mechanism 50 is arranged in the area of the fulcrum 8 of the pedestal 6, one end 50a of which is pivoted to the pedestal 6 inside the bend, and the other end 50b
is pivotally connected to a portion 52 of the swinging arm 5 supported on the frame 6. Therefore, since the part 52 of the platform 6 or the swinging arm 5 extending from the fulcrum 8 to the point of action of the hydraulic mechanism forms a triangle with the hydraulic mechanism 50,
When the hydraulic mechanism 50 protrudes, the swinging arm 5 is lifted.

As shown, the swinging arm 5 consists of two parts 51 and 52, of which the part 51 carrying the roll 4 is constructed in a straight line, while the part 52 connected to the pedestal 6 is arranged at an angle β. It consists of two straight pieces 52a and 52b that are rigidly connected to each other. In this case, the angle β is approximately 135°. In the embodiment according to FIG. 11, the frame 6 also consists of two linear pieces 6a and 6b rigidly connected to each other, of which the lower piece 6a stands upright and has a fulcrum 8 of the swinging arm 5. The second piece 6b is connected to the above piece 6a at an angle γ. This second piece 6b is directed outwardly away from the roll 4, and the angle γ between the two pieces 6a and 6b is approximately 150°. In this way, because the part 52 on the one hand and the frame on the other hand are angular, a particularly advantageous introduction and utilization of the forces by the hydraulic mechanism 50 is possible.

11 and 12 furthermore show a particularly preferred operating mechanism for reversing the direction of rotation of the roll 4. FIG. The operating mechanism consists of a push rod 54 movably disposed on a bearing 53 of an individual piece 52a.
An end 54a on the side closer to the hydraulic mechanism 50 protrudes beyond the portion 52 and is provided with a cam 55 for operating the limit switch 56 there. The cam 55 can be adjusted on the push rod 54. The limit switch 56 is mounted on a support 57 parallel to the push rod or piece 52a.

Operation of the push rod is effected by an extension 59 which projects beyond the pin joint 58 between parts 51 and 52. The extension 59 is pivotally connected to an intermediate rod 60, the other end of which is pivotally connected to the corresponding end 54b of the push rod 54.

Accordingly, when the linear portion 51 moves from the position of FIG. push in a direction.

The hydraulic mechanism can be operated by a motor or by a hand pump, but a hand pump makes the device less expensive. Note that the use of a hydraulic mechanism makes it possible to provide hydraulic locking, as in the embodiments shown in FIGS. When ascending, the respective ascending positions reached are maintained. Finally, hydraulic devices can also be used to apply additional force to the waste by means of suitable throttling.

[Brief explanation of drawings]

1 is a partial sectional view of an embodiment of the compression device according to the invention, FIG. 2 is a plan view of the configuration according to FIG. 1, FIG. 3 is an enlarged sectional view of the compression roll of the device according to FIG. 1, and FIG. 5 is an enlarged view of the device according to FIG. 4 in the upright position for loading and unloading the rolls; FIG.
Fig. 7 is a further enlarged view of the fulcrum of the swinging arm in the front view shown in Fig. 5; Fig. 8 is a front view shown in Fig. 7 - line; Fig. 9 is an embodiment of the switching mechanism. 10 is a front view according to the lines of FIG. 9, FIG. 11 is a front view of another variant embodiment of the device according to the invention, and FIG. 12 is an enlarged view of a part of FIG. 11. . 1... Container, 2... Garbage, 4... Compression roll, 5... Swinging arm, 6... Frame, L... Extension length of swinging arm.

Claims (1)

[Scope of Claims] 1. A driven compression roll 4 that reciprocates over the garbage 2 in the container 1 is provided, and the roll is rotatably attached to the free end of a swinging arm 5 that is pivotally supported on a pedestal 6. 1. A compression device for garbage in a container with an open top, characterized in that the extension length L of the swinging arm is variable. 2. The compression device according to claim 1, wherein the compression roll 4 is constituted by a hollow cylinder with both end faces closed. 3. The compression device according to claim 2, wherein the compression roll 4 is made of a steel plate. 4 The compression roll 4 has a diameter of about 80 cm, and has a diameter of about 80 cm.
Compression device according to claim 2 or 3, having a weight of 200Kg to 300Kg. 5. The compression device according to any one of claims 1 to 4, wherein the drive means 120, 240 for the compression roll 4 is located inside the roll 4. 6 The driving means 120 and 240 are the spur gear transmission mechanism 2
40, and the spur gear transmission mechanism 240 is connected to the middle part 230 of the roll 4 fixed to the end of the swinging arm 5.
A compression device according to claim 5, wherein the compression device is arranged together with a drive motor 120. 7 The two rotatably supported outer hollow parts 260 and 270 of the roll 4 are connected to the fixed intermediate part 230
A compression device according to claim 6, which is connected to a compressor. 8. The drive motor 120 of the roll 4 is arranged eccentrically with respect to the shaft 250 passing through it, and the drive motor 120 of the roll 4
is actuated by a spur gear transmission mechanism 240 and the drive motor 120 is juxtaposed alongside the shaft 250 and projects into one of the two hollow parts 270. compression equipment. 9. Compression device according to any one of claims 1 to 8, wherein the roll 4 is driven at about 25 revolutions per minute. 10 The fixed intermediate portion 230 of the roll 4 is the transmission mechanism 2
Compression device according to any one of claims 7 to 9, comprising 40 housings or covers for the housings. 11. The compression device according to claim 10, wherein the cover of the housing of the transmission mechanism also constitutes bearing means for the rotatable hollow portions 260, 270 of the roll 4 or its shaft 250. 12. Compression device according to any one of claims 1 to 11, in which the swinging arm 5 consists of a plurality of individual parts 9, 90a that can be inserted into one another in a telescoping manner. 13 The bearing 8 of the swinging arm 5 is equipped with a lifting means 100, and the fulcrum at the upper end of the swinging arm 5 is the lifting means 100.
The compression device according to any one of claims 1 to 12, which is moved up and down by. 14 The sum of the length L of the swinging arm 5 from the upper fulcrum 8 to the lower free end of the swinging arm 5 and half the roll diameter D is slightly smaller than half the length A of the container 1. The compression device according to any one of Items 1 to 13. 15 Limit the lateral movement of roll 4 by means of limit switches, and at each extreme position roll 4
The compression device according to any one of claims 1 to 14, wherein the rotation direction of the compressor is automatically switched. 16 Provide a portion 90a of the swinging arm 5 that protrudes to the opposite side of the roll 4 beyond the fulcrum 8 of the frame 6, and at the position where the swinging arm 5 is rotated, insert the end of the portion 90a on the side opposite the fulcrum 8. 16. The compression device according to claim 1, wherein the connecting rod 180 is pivotally connected to the frame 6 via a chain. 17. Compression according to claim 16, in which the last member 90a of the telescoping hollow body forms an arm projecting beyond the fulcrum 8 to the opposite side, to which a connecting rod 180 or chain is engaged. Device. 18 The frame 6 is located in the center of the container 1 and the arm 17
18. A compression device according to any one of claims 1 to 17, wherein the arm 170 extends above the container 1 and a fulcrum 8 for the swinging arm 5 is arranged at the free end of the arm 170. 19. The compression device according to claim 18, wherein the frame 6 is provided with large substrates 150, 160, the substrates 150, 160 extend below the container 1, and the container 1 is placed thereon. . 20 Interengaging notches and the like are connected to the substrate 15.
20. The compression device according to claim 19, which is provided as a coupling means between the container 1 and the container 1. 21 A stop rail 150a that extends from below to the corresponding end surface 1a of the container 1, with the substrate 150 on the end surface side.
21. A compression device according to claim 19 or claim 20, comprising: the container 1 being in contact with the stop rail in use. 22 When the roll 4 is rotated, the arm 170 is spaced apart from the substrate so that the container 1 can be placed on the substrate 150 diagonally from above and can be pulled away from the substrate 150 in the opposite direction. A compression device according to claim 21. 23. The compression device according to any one of claims 1 to 22, wherein the drive motor 120 is configured as a reverse motor. 24. Claim 2 in which the direction of rotation of the reverse motor is switched manually or by a limit switch operated at each extreme position.
Compression device according to item 3. 25 The deflection angle α of the swinging arm 5 is limited by a stop that interacts with the limit switch, and each time the swinging arm 5 reciprocates, the lifting means 100 of the platform lifts the fulcrum 8 of the swinging arm 5 by a predetermined distance. A compression device according to claim 24, comprising: 26 The elevating means comprises a hydraulic mechanism, and when the swinging arm 5 collides with the stop, the elevating means 100 supports the fulcrum 8 of the swinging arm 5 at the floating position of the elevating means 100. 26. Compression device according to claim 25, characterized in that the portion is moved upwardly. 27. Claims in which a check valve is provided to retain the pressure hydraulic oil displaced during the upward movement and to keep the hydraulic mechanism part of the lifting means 100 supporting the fulcrum 8 in the raised position. Compression device according to clause 26. 28. The compression device according to claim 27, wherein the check valve is also used for lowering the hydraulic mechanism of the lifting means 100. 29. The compression device according to any one of claims 1 to 28, wherein the surface of the roll 4 is roughened or provided with projections 140 transverse to the direction of movement of the roll. 30. The compression device according to claim 29, wherein the protrusion 140 is made of flat steel. 31. The compression device according to claim 29 or 30, wherein the protrusion 140 projects about 15 mm above the roll surface. 32 A cable reel 130 is arranged at the upper free end 90a of the telescopically retractable rocking arm 5, which cable reel 130 is connected to the drive motor 1 of the roll 4.
20, the compression cable according to any one of claims 1 to 31, which is used to supply power to a cable, and is configured to automatically wind up and unwind the cable as the length of the swinging arm changes. Device. 33. At least one rim 290 is arranged at each end of the roll 4 and surrounds the roll 4 in an annular manner, the upper edge of the rim being above the roll surface. The compression device according to any one of Items 32 to 32. 34. The compression device according to any one of claims 1 to 33, wherein both end surfaces of the roll 4 are provided with walls or covers 300 that are curved outward. 35. The compression device of claim 33, wherein the rim 290 comprises a surrounding rubber tire. 36. The swing arm 5 is provided with a pin joint 10 dividing the swing arm 5, and in the area of the pin joint at least one stop 11 is provided to prevent the full extension of the swing arm 5 and to prevent the pin joint from being fully extended. Claims 1 to 11 and 13 to 35, in which two parts 9a, 9b, 9c connected at 10 are sandwiched by an angle α smaller than 180° at a protruding position of the roll 4. The compression device according to any one of the above. 37 A part of the pin joint 10 is configured as a fork 10a, and another joint part engages between the two forks, and the two
A coupling pin 12 passing through the two parts connects these parts, said stop being external to said coupling pin 12 and another pin 11 passing through the outer forked part.
37. A compression device according to claim 36, comprising: 38. Claim No. 3, in which the swinging arm 5 is movable only on one side of the platform 6, and the apex of the angle α formed between the parts 9a, 9b, 9c of the swinging arm 5 is at the top of this range of movement. Compression device according to item 36 or item 37. 39. The compression device according to claim 38, wherein the frame 6 is disposed on the long side of the container 1. 40 Swinging arm 5 has a total of three parts 9a, 9b, 9
The compression device according to any one of claims 36 to 39, wherein the compression device is divided into two parts, and two pin joints 10 are provided between these parts. 41 For loading and unloading the roll 4, the fulcrum 8 of the frame 6
A first portion 9a of the swinging arm 5 that is connected to the swing arm 5 stands up almost vertically, and a second portion 9b is connected to the portion 9a at right angles, and further extends downward at right angles to the end of the second portion 9b. 41. The compression device according to claim 40, wherein the third portion 9c with the driven rolls 4 is suspended. 42 In the area of the pin joint 10 between the first two parts 9a, 9b there is provided a support 31 which overhangs below the second part 9b and which holds the second part 9b relative to the first part 9a. and hold it in a perpendicular position with the support 3
42. The compression device according to claim 41, wherein the second portion 9b is placed on top of the compressor. 43 The lifting means 18 disposed below the fulcrum 8 of the frame 6 acts on the end of the towing rope 19 etc., and the first portion 9a connected to the fulcrum is moved by the towing rope 19 to the end of the swinging arm 5. 1 via a semicircular roller 20 fixed to the part 9a and moving with said part,
Claim 13: being towed in a vertical position
The compression device according to item 41 or 42. 44. The lifting means consists of a rack winch 18, the housing of which is pivotally connected to the rack 6 in its lower region, and the upward free end of the rack 26 is connected to a traction rope 19. A compression device according to claim 43. 45 The first part 9a of the swinging arm 5 aligned with the end of the tow rope 19 facing away from the rack winch 18 on the semicircular roller 20 itself or in the region of the semicircular roller 20 facing away from the rack winch 18.
45. The compression device according to claim 44, wherein the compression device is fixed to. 46. The compression device according to any one of claims 36 to 45, wherein the height of the frame 6 is variable. 47. Compression device according to claim 46, in which the frame 6 consists of two parts 17, 22 which are longitudinally movable relative to each other and which can be fixed in various relative positions. 48 Two parts 17,2 that can be moved vertically relative to each other
48. A compression device according to claim 47, wherein the two are nested into one another. 49 Two nested parts 1
7, 22 are fixed to each other at different heights by means of transverse locking pins which can be inserted into matched recesses 23 of the two parts 17, 22. Compression device as described in Section. 50 A universal joint 25 is attached to the upper movable part 22 of the frame 6.
50. The compression device according to claim 46, wherein the compression device is provided with a universal joint, and the upper end of the rack 26 can be arbitrarily connected to the universal joint. 51 Rope hooks 21 are arranged on the first portion 9a of the swinging arm 5 at intervals corresponding to the vertical intervals of the respective locking holes 23 of the frame 6, and the upper end of the towing rope 19 is attached to the rope hooks 21 at the corresponding height. A compression device according to any one of claims 46 to 50, which can be hooked upon adjustment. 52 For each reverse switching, at least two limit switches 41, 42 are provided, to which a cam 40, which is moved by means of an operating cable 38 against the force of a return spring 48, is provided. At this time, one end 38a of the operating cable 38 is connected to one end of the swinging arm.
23, wherein the other end 38b engages with another part of the swinging arm, and the operating cable 38 is guided to the outside thereof via the pin joint 10. The compression device according to any one of Items 24 and 36 to 51. 53 Claim 5, wherein the operating cable 38 is a flat strip made of wear-resistant plastic.
Compression device according to item 2. 54 Claim 5 in which the operation cable 38 is guided through the stop pin of the pin joint 10
54. The compression device according to item 2 or 53. 55 Operation cable 38 connects each pin joint 1
0, it passes under a guide pin 44 fixed to the trailing parts 9b, 9c of the rocking arm 5, which guides the operating cable 38 to the respective parts 9b, 9c.
55. The compression device according to claim 54, which is adapted to be held near the wall of 9c. 56 A cam 40 is mounted on a guide rod 39 disposed movably on a fixed bearing 46, an operating cable 38 at one end of the guide rod 39 and a return spring 48 configured as a tension spring on the guide rod 39. Claims 23 to 30 engage with the other end, and the cam 40 is movably disposed on the guide rod 39 and can be fixed in the adjusted position of the guide rod. The compression device according to any one of the above. 57 Limit switches 41, 42 are arranged within the range of movement of the cam 40 at the two opposite ends of a switchbox 43, which switches between the bearings 46 of the guide rod 39 and 57. The compression device according to claim 56, wherein the compression device is fixed to the portion 9a of the compressor. 58 A hydraulic mechanism 50 is disposed in the area of the fulcrum 8 of the pedestal 6, one end 50a of the hydraulic mechanism 50 is pivotally attached to the pedestal 6 inside the bent part, and the other end 50b is pivoted to the pedestal 6. Portion 5 of swinging arm 5 supported on pedestal 6
37. The compression device according to claim 36, wherein the pedestal 6 and a part of the swinging arm 5 form a triangle together with the hydraulic mechanism 50. 59 The swinging arm 5 consists of two parts 51 and 52, of which the part 51 that carries the roll 4 is formed in a straight line, and the part 52 that connects to the frame 6 has an angle β.
Two linear pieces 5 rigidly connected to each other by sandwiching the
59. A compression device according to claim 58, comprising: 2a, 52b. 60 The angle β between the two pieces 52a and 52b is approximately
60. The compression device of claim 59, wherein the angle is 135°. 61 The frame 6 also consists of two linear pieces 6a and 6b that are rigidly connected to each other, of which the lower piece 6
a stands upright, and a second piece 6b having a fulcrum 8 of the swinging arm 5 is connected to the lower piece 6a and directed outward away from the roll 4, and the two pieces 6a, 61. A compression device according to any one of claims 58 to 60, wherein the angle γ between 6b is approximately 150°. 62 connecting to the part 51 carrying the roll 4;
First piece 52a of first portion 52 of swinging arm 5
has a bearing 53 for the push rod 54 parallel to the piece 52a, and the end of the push rod 54 on the side closer to the piece 52b connected to the fulcrum 8 protrudes beyond the first piece 52a, and Claim 1, characterized in that two adjustable cams 55 are provided at the above-mentioned protruding locations for operating a limit switch 56 fixed to a support 57 disposed on the individual piece 52a. The compression device according to any one of items 58 to 61. 63 The straight portion 51 of the swinging arm 5 is the pin joint 58
is provided with an extension 59 projecting beyond the pin joint 58 in the region of , and an intermediate rod 6 at the end of the extension 59.
63. A compression device as claimed in claim 62, in which the extension 59 is pivoted and the other end of the extension 59 is pivoted to the corresponding end of the push rod 54.