CN221136469U - Tension mechanism, wire saw unit and wire cutting machine - Google Patents

Abstract

The utility model relates to the technical field of wire cutting, and particularly provides a tension mechanism, a wire saw unit and a wire cutting machine, wherein the tension mechanism comprises a tension wheel, and the tension wheel can at least generate motion around a first axis based on torque provided by a driving part; in a second aspect, at least the tension pulley is movable about a second axis under the influence of an external force; wherein the first axis and the second axis are not coplanar and have an included angle therebetween. On the basis, the tension mechanism is arranged between the take-up and pay-off mechanism and the cutting mechanism of the wire cutting machine, so that the running reliability and the cutting quality of the wire cutting machine are guaranteed on the premise that the wire arranging wheel and the reversing wheel are omitted.

Description

Tension mechanism, wire saw unit and wire cutting machine

Technical Field

The utility model relates to the technical field of wire cutting, and particularly provides a tension mechanism, a wire saw unit and a wire cutting machine.

Background

A wire cutting machine is a device for cutting a workpiece (such as a silicon rod (including a single crystal silicon rod, a polycrystalline silicon ingot, etc.), a sapphire rod, a magnetic rod, a semiconductor rod, etc.) of a hard and brittle material, such as cutting, squaring, slicing, etc., by using a cutting wire (such as a diamond wire, etc., which is a cutting steel wire with diamond fine particles embedded in the surface thereof).

Taking a slicing machine for slicing a photovoltaic silicon rod (silicon rod for short) as an example, the slicing machine directly operates the silicon rod through a cutting mechanism, and in a normal situation, the wire cutting machine mainly comprises three cutting main rollers (two upper and one lower) distributed in an inverted triangle form, dense annular grooves are processed on the cutting main rollers, and a wire net capable of continuously cutting the silicon rod can be formed by densely winding diamond wires at positions corresponding to the annular grooves. In this way, the diamond wire between the two upper main cutting rolls can cut the workpiece by the reciprocating movement of the diamond wire between the cutting mechanism and other structures of the wire cutting machine such as the take-up and pay-off rolls.

In the slicer of the prior art, the diamond wire is arranged between the winding rollers of the left winding mechanism and the right winding mechanism, and the cutting mechanism of the slicer usually comprises two or three main rollers, namely a first main roller at the upper left, a second main roller at the upper right and a third main roller at the lower part. In addition, the slicer comprises at least six guide wheels (three are respectively arranged on the left side and the right side), and the three guide wheels are respectively a winding displacement wheel, a tension wheel and a reversing wheel by taking the left side as an example. Based on this structure, the wire winding route of slicer is: for example, the left winding roller (taking the winding roller as a paying-off roller (in this case, the right winding roller is a winding roller), obviously, the function of the winding roller can be switched between the winding roller and the paying-off roller, if the left winding roller is the winding roller, the right winding roller is correspondingly switched to the paying-off roller), the left winding roller (winding wheel, tension wheel and reversing wheel), the main roller three, the main roller two, the main roller one, the main roller three (winding for forming a wire net for a plurality of times), the right winding roller (reversing wheel, tension wheel and winding wheel), and the right winding roller.

Based on this, the inventors have purposely proposed a product form that reduces the number of guide wheels. This is because: the product form of reducing the number of the guide wheels not only can reduce the input cost of a user side in the aspects of guide wheel consumable materials and the like, but also can reduce the distance from the main roller to the winding roller of the diamond wire. On the basis, the negative influence caused by extra tension due to factors such as inertia of the diamond wire, friction resistance of the guide wheels, bending stress of the diamond wire bypassing the guide wheels, torsion stress of the diamond wire caused by non-ideal coplanarity among the guide wheels and the like in the operation process of the diamond wire is hopefully reduced, and therefore the cutting quality of the slicer is improved. Obviously, the method has great significance for the application of ultrafine line and high line speed of the future microtome.

However, how to ensure the operational reliability and cutting quality of the slicer is a technical problem that must be faced when a product form is proposed that reduces the number of guide wheels.

Therefore, there is a need in the art for a new solution to the above technical problems.

Disclosure of utility model

The present utility model aims to solve at least in part the above-mentioned technical problems, and in particular, to solve the technical problems of how to ensure the operational reliability and cutting quality of the microtome as much as possible when proposing a product form with a reduced number of guide wheels.

In a first aspect, the present utility model provides a tension mechanism comprising a tension wheel, the tension wheel being capable of generating movement about a first axis based at least on torque provided by a drive member; in a second aspect, at least the tension pulley is movable about a second axis under the influence of an external force; wherein the first axis and the second axis are not coplanar and have an included angle therebetween.

With such a configuration, it is possible to achieve a partial function in the traverse corresponding to the conventional six-guide structure on the basis of ensuring the level of tension of the cutting wire wound therearound by the cooperation of the motions related to the two axes. The method can be as follows: when friction and thus stress is created between the cutting wire and the wall of the wire groove due to its positional deflection within the wire groove, this friction is reduced at least by rotation of the tension pulley about the second axis.

It will be appreciated that the size of the angle between the first axis and the second axis and the relative positional relationship when forming the angle, the source of the force/moment required by the tension pulley to produce movement about the two, the manner of synthesizing movement achieved by the cooperation of the two, etc. may be determined by one skilled in the art according to actual requirements. Such as having a first axis and a second axis. For example, the tension wheel may be moved about the first axis by an external force (such as an external force accompanying deflection of the cutting wire) generated during operation of the wire cutting machine, for example, in addition to the drive member, either by movement of the tension wheel about the first axis alone or by movement of the tension wheel in synchronization or non-synchronization with other associated structures. Similarly, the external force that causes the tension pulley to move about the second axis may be an external force that is generated when the wire cutting machine is in operation (e.g., an external force that accompanies deflection of the cutting wire), or an external force that may be applied by a driving member such as the one described above or other driving members.

Illustratively, the forces that cause the tension wheel to generate motion about the first/second axis each include external forces from the drive component and the wire cutting machine that are generated in operation. The tension pulley may be moved about the first/second axis in any reasonable posture, or alternatively, any reasonable relative positional relationship between the centerline of the tension pulley and the first/second axis may be provided, such as being coincident, parallel, or having an included angle, etc.

Furthermore, the specific form of the driving means can be determined by the person skilled in the art according to the actual requirements, such as a motor, a rotating module or a rotating assembly realized by means of a power cylinder (hydraulic cylinder, air cylinder, electric cylinder, etc.) and a corresponding transmission mechanism.

For the above-mentioned tensioning mechanism, in one possible embodiment, the tensioning mechanism comprises a connection assembly by which the tensioning wheel is connected to the drive member and thus generates a movement about the first axis based on a torque provided by the drive member.

By such a construction, a possible way of achieving a driving connection between the driving member and the tension pulley is given.

It will be appreciated that the connection assembly may comprise one or more components, and that the connection assembly may be fixedly or movably connected to the tension wheel. Illustratively, the connecting assembly comprises a plurality of components, wherein (at least one part of) the components are fixedly connected or movably connected, and the components which are in butt joint with the tension wheel in the connecting assembly are fixedly connected or movably connected with the tension wheel.

With respect to the tension mechanism described above, in one possible embodiment, the connection assembly comprises a first connection part and a second connection part, the first connection part being connected to the drive part, the tension wheel being pivotally arranged to the second connection part, wherein the first connection part is in rotational connection with the second connection part, so that: the tension wheel is capable of generating a rotational movement about the second axis based at least on the rotational connection.

By means of this construction, possible configurations of the connection assembly are given.

It will be appreciated that the person skilled in the art may determine the structural form of the first/second connection member, the specific manner in which the two are connected in rotation, etc. according to the actual requirements. Illustratively, both are rotational connections that are directly implemented based on their own structure or that are implemented in dependence on the relevant structure/mechanism, etc.

With the above-mentioned tension mechanism, in one possible embodiment, the first connecting member is formed with an installation space provided with a rotation shaft, and the second connecting member is rotatably connected with the first connecting member through the rotation shaft.

By means of this construction, a possible design is provided in which the first connecting part and the second connecting part are connected in a rotationally fixed manner.

It is understood that a person skilled in the art may determine the specific form of the installation space, the specific manner in which the rotation shaft is disposed in the installation space, the implementation manner of the rotation connection, etc. according to actual requirements. Illustratively, the second connecting member is fixedly connected with the rotating shaft, the rotating shaft is movably connected with the first connecting member, and the like.

With the above-described tensioning mechanism, in one possible embodiment, the first connecting part comprises a vertical portion which is in driving connection with the drive part on the one hand and which extends or is provided with a transverse portion on the other hand, which transverse portion forms the installation space.

By means of this construction, a possible design of the first connecting part is provided.

It should be noted that the vertical and horizontal directions are understood to be structures that are substantially vertical and substantially horizontal, and the present tension swing rod of the six-guide-wheel structure is used as a vertical portion and modified, such as extending the horizontal portion in an integrally formed manner, for example.

With respect to the tension mechanism, in one possible embodiment, the rotating shaft is fixedly disposed at a position of the first connecting portion corresponding to the installation space, and the second connecting member is rotatably connected with the rotating shaft.

With such a construction, a specific implementation of the rotational connection between the first connection part and the second connection part is given.

With respect to the tension mechanism, in a possible implementation manner, the transverse portion includes a first mounting end and a second mounting end, and two ends of the rotating shaft are respectively disposed at the first mounting end and the second mounting end.

By means of this construction, a possible construction of the transverse portion is provided.

It will be appreciated that the structural form of the first/second mounting ends and the specific manner of forming the transverse portion thereof may be determined by those skilled in the art according to actual needs, for example, the two may be directly formed into the transverse portion or may be formed into the transverse portion by being disposed on a base, the first/second mounting ends may be plate-like structures, block-like structures, or the like, and the structures of the two may be the same or different.

For the above-mentioned tensioning mechanism, in one possible embodiment, the first mounting end and/or the second mounting end is provided with an open structure via which the spindle can enter the mounting space.

With such a construction, a possible implementation of the mounting of the spindle to the transverse portion is given. Such as slots, openable slits, etc. in the open structure. Illustratively, under the action of external force, the rotating shaft can be extruded into the installation space through the slots under the action of external force, and then the external force is removed, and the slots are automatically retracted.

For the tension mechanism, in one possible embodiment, the first connecting component includes a limiting structure, and the rotating shaft can be fixedly disposed in the installation space through the limiting structure.

Through such constitution, can seek to guarantee the installation reliability of pivot, if limit structure can be direct with the pivot cooperation, with the adaptation structure cooperation of processing in the pivot or need introduce other structures such as fastener, if realize the fixed connection of pivot through fastener, limit structure and the cooperation of pivot. Such as the spacing structure may be, holes, slots, protrusions, etc.

For the tension mechanism, in one possible embodiment, the limiting structure is disposed at the first mounting end and/or the second mounting end.

By such a constitution, a setting mode of the limit structure is given.

For the tension mechanism, in one possible implementation manner, the tension mechanism comprises a bearing box, the rotating shaft is arranged in the bearing box in a penetrating manner, and the second connecting component is fixedly connected with or integrally formed with the bearing box.

By such a construction, a specific way of realizing the rotational connection of the second connection member with the rotation shaft is given.

For the above-mentioned tension mechanism, in a possible embodiment, the second connection member includes a connection arm, and the tension pulley is pivotally disposed on the connection arm, and the connection arm is fixedly connected to the bearing housing or integrally formed therewith.

By means of this construction, a possible design of the second connecting part is provided.

It will be appreciated that the structural form, number and connection manner of the connecting arms and the bearing housing can be determined by those skilled in the art according to actual requirements. The connecting arms comprise a first vertical connecting arm and a second horizontal connecting arm, the tension wheel is pivoted on the first vertical connecting arm, the first connecting arm is fixedly connected with the second connecting arm or integrally formed, and the second connecting arm is fixedly connected with the bearing box or integrally formed.

With the above-described tension mechanism, in one possible embodiment, the second connecting member is provided with a weight assembly.

With this configuration, it is possible to ensure that the center of gravity is always maintained on the second axis during rotation of the tension pulley about the second axis.

It is understood that the structural form, number, arrangement position and arrangement mode of the counterweight assembly can be determined by those skilled in the art according to actual requirements, and can be a fixed structure or a movable structure. Such as the configuration component may be provided on the second connecting member or may be provided on other components such as the bearing housing that deflect with the second connecting member.

With respect to the tension mechanism described above, in one possible embodiment, at least a portion of the weight assembly is a movable structure.

With this configuration, the weight distribution form of the counterweight assembly can be adjusted by the movement of the structure.

It will be appreciated that the movable form of the counterweight assembly can be determined by those skilled in the art according to actual needs, such as movement, rotation (rotation, revolution), a combination of the two, and the like. For example, it may be moved in a cross direction.

For the tension mechanism described above, in one possible embodiment, the counterweight assembly includes: the counterweight block is arranged on the counterweight rod, and the counterweight rod is arranged on the second connecting component in a direct or indirect mode; wherein the balancing weight can move along the axial direction of the balancing weight rod and/or around the circumferential direction of the balancing weight rod.

For the tension mechanism described above, in one possible embodiment, the counterweight assembly includes: an adjusting member capable of applying an external force to the weight lever so as to: the balancing weight moves along the axial direction of the balancing weight rod under the action of the external force.

With this configuration, the weight can be moved in the axial direction of the weight shaft by applying an external force to the adjusting member.

It is understood that the structural form, the number of the adjusting components, the direction of the force applied by the adjusting components to the balancing weights and the like can be determined by a person skilled in the art according to actual requirements. Illustratively, the weight is arranged transversely, two telescopic adjusting parts are arranged on two sides of the weight along the arrangement direction, and the weight moves rightwards under the condition that the left adjusting part extends and the right adjusting part retracts. And vice versa to the left. Any reasonable structure or mechanism can be selected by those skilled in the art on the premise that telescopic movement can be achieved.

For the tension mechanism described above, in one possible embodiment, the weight bar includes one or more; and/or the adjustment member is an adjustment screw.

For the tension mechanism described above, in one possible embodiment, the weight is capable of helical movement along the weight rod.

With such a construction, a specific form of the counterweight assembly to effect its movability is given.

For the tension mechanism described above, in one possible embodiment, the weight includes at least one, wherein in a case where the weight includes a plurality of weights, the installation directions of the weight bars corresponding to the plurality of weights are the same or different and/or the weights are directly or indirectly provided to the second connection member through the weight bars.

By such a construction, a possible form of construction of the counterweight assembly is given.

For the tension mechanism, in one possible implementation manner, the balancing weights include a first balancing weight and a second balancing weight, the first balancing weight is arranged on the second connecting component through a balancing weight rod, and the second balancing weight is arranged on the first balancing weight through a balancing weight rod, wherein an included angle is formed between the balancing weight rods corresponding to the first balancing weight and the second balancing weight.

With such a construction, a specific construction of the counterweight assembly is given.

It will be appreciated that the size of the included angle between the two weight bars may be determined by those skilled in the art according to actual needs, and may be perpendicular to each other or at any reasonable angle.

For the tension mechanism described above, in one possible embodiment, the second connecting member or the structure moving with the second connecting member is provided with a weight seat, and the weight assembly is provided to the weight seat.

With this construction, a possible form is given in which the counterweight assembly is provided to the second connecting member.

With the tension mechanism described above, in one possible embodiment, the weight seat is provided with a weight mounting member or formed with a weight mounting structure, and the weight assembly is provided to the weight mounting member or the weight mounting structure.

With such a construction, a possible implementation of the counterweight assembly arranged at the counterweight seat is given.

It will be appreciated that the specific form of the weight mounting member/structure may be determined by one skilled in the art based on actual requirements, such as a block structure, a disc structure, a mounting bracket, etc.

For the tension mechanism described above, in one possible embodiment, the tension pulley has a wire groove around which a cutting wire can be wound, the second axis being in the plane of the wire groove or the second axis being parallel to the plane of the wire groove.

With this configuration, a specific internal relative positional relationship of the tension mechanism is given.

For the tension mechanism described above, in one possible embodiment, the first axis is perpendicular to the second axis.

With this configuration, a specific internal relative positional relationship of the tension mechanism is given.

In a second aspect, the present utility model provides a wire saw unit comprising a tension mechanism according to any one of the preceding claims.

It will be appreciated that the wire saw unit has all the technical effects of the tension mechanism described in any of the foregoing, and will not be described in detail herein.

For the above wire saw unit, in one possible embodiment, the wire saw unit includes a wire takeup and paying out mechanism and a cutting mechanism, and the tension mechanism is disposed between the wire takeup and paying out mechanism and the cutting mechanism.

By such a construction, a possible construction of the wire saw unit is given.

In a third aspect, the present utility model provides a wire cutting machine comprising a tensioning mechanism or a wire saw unit as defined in any one of the preceding claims.

It will be appreciated that the wire cutting machine has all the technical effects of the tension mechanism described in any one of the foregoing, and will not be described in detail herein.

For the wire cutting machine described above, in one possible embodiment, the wire cutting machine is a microtome.

With this construction, a specific structural form of the wire cutting machine is given.

Drawings

The preferred embodiments of the present utility model will be described below by taking a silicon rod to be cut (hereinafter, abbreviated as a silicon rod) as a workpiece, and a wire cutting machine as a slicer as an example, and referring to the accompanying drawings, in which:

FIG. 1 shows a schematic view of the slicer according to one embodiment of the present utility model;

FIG. 2 is a schematic view showing the structure of a tension mechanism of the microtome according to the prior art;

fig. 3 is a schematic diagram showing the working principle of a tension mechanism of a microtome according to the prior art;

FIG. 4 shows a schematic diagram of the tension mechanism of the microtome according to one embodiment of the present utility model;

FIG. 5 is a schematic diagram II of a tension mechanism of a microtome according to one embodiment of the present utility model, showing a tension swing link;

FIG. 6 illustrates a schematic (partially cut away) view of the tension mechanism of the microtome in accordance with one embodiment of the present utility model showing the spindle, bearing housing, rotating arm and tension pulley;

FIG. 7 is a schematic diagram of a tension mechanism of a microtome according to one embodiment of the present utility model showing the relationship between the second axis and the plane of the wire slot of the tension pulley;

FIG. 8 illustrates a schematic view of the construction of a counterweight assembly in the tension mechanism of the microtome according to one embodiment of the utility model;

FIG. 9 illustrates a schematic diagram of a state of a yaw movement assembly of a microtome according to one embodiment of the present utility model;

FIG. 10 illustrates a second schematic view of the state of the yaw movement assembly of the microtome according to one embodiment of the present utility model;

FIG. 11 illustrates a third schematic view of the state of the yaw movement assembly of the microtome according to one embodiment of the present utility model;

FIG. 12 illustrates a schematic diagram of a state of a deflection motion assembly of a microtome according to one embodiment of the utility model; and

Fig. 13 shows a second schematic view of the state of the deflection motion assembly of the microtome according to one embodiment of the utility model.

List of reference numerals:

04. a tension wheel; 041. a tension motor (conventional example); 042. tension swing rod (existing example);

100. A slicer;

21. a first take-up and pay-off mechanism; 211. a wire winding and unwinding roller; 22. a second take-up and pay-off mechanism;

31. a first cutting main roller; 32. a second cutting main roller; 33. a third cutting main roller;

41. A first tension mechanism; 42. a second tension mechanism;

5. a threading mechanism; 51. wiring grooves;

61. A tension wheel; 611. a wire slot; 62. a tension motor; 621. a motor base;

63. Tension swing rod;

631. A vertical portion; 632. a lateral portion; 633. an installation space; 634. a rotating shaft; 6341. a through hole; 6351. a first mounting end; 6352. a second mounting end; 636. an open slot; 637. a limiting hole; 638. a bearing housing;

64. a rotating arm;

651. a first axis; 652. a second axis;

7. a counterweight assembly;

71. A counterweight seat; 711. a counterweight mounting block; 712. a weight reduction groove;

721. a first balancing weight; 722. a second balancing weight;

731. a first weight bar; 732. a second weight bar;

74. an adjusting screw;

8. a diamond wire;

9. a silicon rod;

10. A distance measuring sensor.

Detailed Description

Preferred embodiments of the present utility model are described below with reference to the accompanying drawings. It should be understood by those skilled in the art that these embodiments are merely for explaining the technical principles of the present utility model, and are not intended to limit the scope of the present utility model. For example, although the present embodiment is described in connection with the rotation shaft being fixed, the rotation arm being fixedly connected to the bearing housing and thus being rotatably connected to the rotation shaft, it is obvious that a person skilled in the art can flexibly adjust the rotation shaft according to actual needs, such as rotation of the rotation shaft, the rotation arm being fixedly connected to the rotation shaft, etc. In addition, on the premise of not influencing the operation reliability of the slicing machine, the movement corresponding to the first axis and the movement corresponding to the second axis can meet the requirements of ensuring tension stability and timely deflection arrangement in a synthetic mode. Such as the first axis and the second axis may not be limited to perpendicular or the like.

It should be noted that, in the description of the present utility model, terms such as "center," "upper," "lower," "left," "right," "vertical," "horizontal," "inner," "outer," and the like indicate directions or positional relationships based on the directions or positional relationships shown in the drawings, which are merely for convenience of description, and do not indicate or imply that the apparatus or elements must have a specific orientation, be constructed and operated in a specific orientation, and thus should not be construed as limiting the present utility model. Furthermore, the terms "first," "second," and the like, are used for descriptive purposes only and are not to be construed as indicating or implying relative importance.

Furthermore, it should be noted that, in the description of the present utility model, unless explicitly specified and limited otherwise, the terms "mounted," "configured," and "connected" are to be construed broadly, and may be, for example, fixedly connected, detachably connected, or integrally connected; can be directly connected, can be indirectly connected through an intermediate medium, and can also be communicated with the inside of two elements. The specific meaning of the above terms in the present utility model can be understood by those skilled in the art according to the specific circumstances.

Furthermore, in the following detailed description, numerous specific details are set forth in order to provide a thorough understanding of the present utility model, it will be appreciated by those skilled in the art that the present utility model may be practiced without some of these specific details. In some instances, principles of microtomes, etc., well known to those skilled in the art have not been described in detail in order to facilitate a salient point of the present utility model.

Three of the devices of the wire cutting machine are in the form of a cutter, a squarer and a slicer, taking a silicon rod as an example of a workpiece to be processed, wherein the cutter is mainly used for cutting a longer silicon rod into a silicon rod with a shorter length (such as a silicon rod with a circular cross section generally, for short, a round rod), and specifically, cutting one silicon rod into a plurality of sections by cutting along the radial direction of the silicon rod. The squaring machine is mainly used for cutting a round bar into a silicon bar with a rectangular (such as square) cross section (the square bar is short, such as the square bar at the stage is not subjected to grinding processing and can be commonly called a rough bar), and specifically, the round bar is cut into the square bar by removing the edge skin of the round bar in the axial cutting mode of the silicon bar. The slicing machine is mainly used for densely and continuously cutting square bars with standard precision (such as square bars at the stage of grinding and processing, which can be commonly called as finished bars) along the radial direction of the square bars in a multi-wire cutting mode so as to obtain sheets to be used. The present utility model is described mainly with respect to a wire cutting machine using a wire-mesh slicer as an example.

Referring generally to fig. 1 and 4, fig. 1 shows a schematic structural view of a microtome according to one embodiment of the present utility model, and fig. 4 shows a schematic structural view of a tension mechanism of a microtome according to one embodiment of the present utility model. As shown in fig. 1 and 4, in one possible embodiment, the wire saw unit of the slicing machine 100 mainly includes a first wire receiving and releasing mechanism 21 and a second wire receiving and releasing mechanism 22 on the left and right sides, the main structure of the first/second wire receiving and releasing mechanism being a wire receiving and releasing roller by which a diamond wire as a cutting wire can realize a wire receiving and releasing function (the wire receiving and releasing function can be interchanged). Wherein the cutting area of the microtome is provided with a cutting mechanism 3, as in the present example comprising a first cutting main roller 31, a second cutting main roller 32 and a third cutting main roller 33 distributed in an inverted triangle, wherein the cutting main rollers (31, 32) are located above the third cutting main roller 33. A first tension mechanism 41 and a second tension mechanism 42 are respectively arranged between the cutting mechanism 3 and the first winding and unwinding mechanism 21 and the second winding and unwinding mechanism 22, and winding and unwinding rollers of the two winding and unwinding mechanisms are lower than tension wheels of the tension mechanisms on the same side. In this way, by the reciprocating movement of the diamond wire between the two wire take-up and pay-off rollers, the tension wheels on the corresponding sides and the cutting mechanism, the silicon wafer can be obtained by cutting the silicon rod along the radial direction of the silicon rod. Specifically, the diamond wire wound by the take-up and pay-off roller with the 'pay-off' function is guided to a cutting mechanism consisting of cutting main rollers (31, 32 and 33) through corresponding side tension wheels, and then guided to the take-up and pay-off roller with the 'take-up' function through another tension wheel, and the take-up and pay-off rollers on two sides alternately take-up and pay-off. On this basis, the silicon rod 9 moving downward can be cut by the wire web of the diamond wire 8 moving between the cutting main rollers (31, 32) located above. Furthermore, the wire saw unit further comprises two threading mechanisms 5 corresponding to the first and second tension mechanisms 41 and 42, one end of which is fixedly connected to the first/second tension mechanism of the respective side and the other end of which extends into the cutting area. The threading mechanism 5 is provided with a wire groove 51 capable of freely accommodating a diamond wire. Taking a take-up and pay-off roller as an example, the diamond wire on the take-up and pay-off roller is wound on a tension wheel and then enters a cutting chamber of the slicer through the wire groove 51.

In contrast to the prior art microtome of six-roller construction mentioned in the background section, the wire-laying wheel and reversing wheel are omitted in the structural form of the microtome of the embodiment and the microtome is modified to a two-roller construction. Based on this structure, it is still assumed that the left winding roller is a take-up roller (the right winding roller is a pay-off roller at this time), and the winding path of the slicer is: left winding roller-left tension roller-third main roller-second main roller-first main roller-third main roller (winding to form net for many times), right tension roller-right winding roller, and only two guide wheels pass through the finished winding path. In order to ensure the reliability of the slicer, the functions corresponding to the conventional wire arranging wheel and the reversing wheel still need to be maintained. In the present utility model, this is achieved mainly by improving the first/second tension mechanism. The first tension mechanism (hereinafter simply referred to as a tension mechanism) will be described below as an example.

Referring to fig. 2 and 3, fig. 2 is a schematic diagram showing a structure of a tension mechanism of a microtome according to the related art. Fig. 3 is a schematic view showing the operation principle of a tension mechanism of the microtome according to the prior art. As shown in fig. 2 and 3, the tension mechanism of the prior art mainly includes a tension pulley 04 and a driving transmission mechanism thereof, and the driving transmission mechanism mainly includes a tension motor (prior art) 041 and a tension swing rod (prior art) 042 (for convenience of description, reference numerals different from the present utility model are used for describing components of the prior art), and the tension motor outputting constant torque can be balanced with an initial tension value of the diamond wire, so that when the tension on the diamond wire changes, the tension change on the diamond wire can be buffered by the left-right swing of the tension swing rod (around the tension swing axis), thereby maintaining the tension on the diamond wire in a relatively stable state. Specifically, during operation of the tension mechanism, the tension motor continuously outputs a constant torque, taking the case of diamond wire winding leftwards, the tension wheel is subjected to a rightward force F (constant torque M/length of the tension swing rod) due to the constant torque M output by the tension motor, and leftward pulling forces (respectively denoted as F1 and F2) are generated on the diamond wire wound around the tension wheel. When the cutting main roller rotation speed is matched with the winding roller rotation speed (balance state), F1, +f2=f, so the tension swing rod cannot swing (is in zero position). When the rotating speed of the cutting main roller is not matched with that of the winding roller, the situation that the resultant force of F1 and F2 is different from F occurs, at the moment, if F1+F2> F, the tension swing rod swings leftwards, and if F1+F2< F, the tension swing rod swings rightwards so as to buffer the tension change of the diamond wire. At the moment, the encoder on the tension motor can capture and recognize the left/right swing gesture of the tension swing rod, and based on the gesture, the tension on the diamond wire can be balanced by adjusting the rotating speed of the winding roller, so that the tension swing rod is restored to the zero position.

Referring mainly to fig. 4, in one possible embodiment, the tension mechanism mainly includes a tension wheel 61, a tension motor 62 as a driving component, and a connection assembly including a tension swing rod 63 as a first connection component and a rotating arm 64 as a second connection component, the tension motor 62 is disposed on a motor base 621, the tension wheel 61 is in driving connection with the tension swing rod 63, the tension swing rod 63 and the rotating arm 64 are in rotating connection, and the tension wheel 61 is pivotally disposed on the rotating arm 64 so that the tension wheel can rotate freely relative to the rotating arm 64 under the driving of the diamond wire and thus ensures the reciprocating motion of the diamond wire. In this way, based on the constant torque provided by the tension motor, when the tension of the diamond wire changes, the tension wheel swings around the first axis 651 (called a tension deflection axis), and when the tension wheel is stressed due to the deviation of the diamond wire in the wire groove, the tension wheel drives the rotating arm to rotate around the second axis 652 (called a tension deflection axis) relative to the tension swing rod, so that friction generated between the diamond wire and the groove wall of the wire groove of the tension wheel due to the deviation of the diamond wire is reduced through the rotation, and the probability of risks such as abrasion of the diamond wire, the groove removal of the diamond wire, the wire breakage and the like caused by friction between the diamond wire and the groove wall of the tension wheel is reduced, and the cutting quality of the slicer is facilitated to be improved. In this example, the tension deflection axis and the tension deflection axis are substantially perpendicular. As with the orientation of fig. 4, the tension deflection axis is located above the tension deflection axis.

Referring mainly to fig. 4 to 7, in one possible embodiment, the tension swing link 63 is of a generally inverted T-shaped structure and includes a vertical portion 631 and a lateral portion 632, the power output shaft of the tension motor is assembled to the vertical portion at a position near the upper end, the vertical portion extends with the lateral portion near the lower end and the lateral portion forms the installation space 633. The rotating arm realizes the rotation of the rotating arm relative to the tension swing rod by means of the assembly relation in the installation space. In this embodiment, a rotating shaft 634 is fixedly disposed in the installation space, and a rotating arm is rotatably connected with the rotating shaft 634. For example, the rotating arm can be directly connected with the tension swing rod in a rotating way.

In this example, the lateral portion is formed with an open mounting space 633 so that the rotary shaft can be directly mounted to the lateral portion of the tension swing link based on the open structural design. Illustratively, the transverse portion is provided with a first mounting end 6351 and a second mounting end 6352 at mounting locations corresponding to two ends of the shaft, respectively, with an open structure (e.g., an open slot 636, etc.) formed at the mounting ends, and the shaft is directly introduced into the mounting space via the open slot 636 to thereby enable mounting thereof on the transverse portion. On this basis, by fixing the rotation shaft 634 to the installation space, the rotation of the rotation arm relative to the tension swing link is achieved by the rotational connection of the rotation arm 64 and the rotation shaft 634.

Illustratively, the manner in which the shaft is secured to the mounting space is: a pair of limiting holes 637 are respectively arranged at the (first and second) mounting ends, and correspondingly, a pair of blind holes 6341 corresponding to the limiting holes are arranged on the rotating shaft 634, so that the fixing of the two ends of the rotating shaft at the (first and second) mounting ends can be realized by means of the cooperation between the fastener and the limiting holes and the blind holes. If the pair of blind holes can be replaced by a through hole, the fixing of the rotating shaft 634 on the tension swing rod 63 can be realized by penetrating the pair of limiting holes and the through hole between the limiting holes by the fastener.

It should be understood that the above manner of fixing the rotating shaft to the installation space is only an exemplary description, and those skilled in the art can determine the specific manner in which the fixing of the rotating shaft and the installation space can be achieved according to actual needs. Such as through the cooperation between the end of the rotating shaft and the tension swing rod, through processing any other matched structures (such as tooth meshing and the like) which can prevent the radial escape of the rotating shaft and the axial movement at the positions of the rotating shaft and the tension swing rod, and the like.

In one possible embodiment, the rotating arm 64 is an arm extending in a substantially vertical direction, an upper end of the rotating arm is rotatably connected to a rotating shaft provided in the installation space, and the tension pulley is pivotally provided at a lower end of the rotating arm.

In one possible embodiment, the rotating arm is rotatably connected to the rotating shaft disposed in the installation space in the following manner: the bearing housing 638 is disposed in the installation space, the rotating shaft 634 is disposed in the bearing housing in a penetrating manner, and the rotating arm 64 is fixedly connected with or integrally formed with the housing of the bearing housing. In this way, the rotary connection between the rotary arm 64 and the tension swing link 63 can be achieved through the rotary support of the bearing.

In this example, the rotating arm is a straight arm in the vertical direction, and therefore the axis of rotation of the bearing housing (the axis of the rotating shaft) is not in the plane of the wire groove 611 of the tension pulley 61 but is parallel thereto. Specifically, the axis of the rotating shaft is located on one side (left side in fig. 7) of the plane where the wire groove is located, which is close to the tension swing rod. For example, the straight arm can be replaced by an L-shaped or inclined arm with a certain included angle with the vertical direction, and the relative position between the straight arm and the inclined arm can be changed.

In order to ensure that the gravity center of a swinging structure (rotating arms and the like except the tension pulley) comprising the tension pulley can fall on a tension deflection axis in the swinging process, thereby avoiding the phenomenon of groove removal and eccentric wear of a diamond wire caused by the gravity center falling on the tension deflection axis, a counterweight assembly is arranged for the tension mechanism.

Referring primarily to fig. 4 and 8, in one possible embodiment, the counterweight assembly 7 includes a counterweight housing 71 and first 721 and second 722 counterweights disposed on the counterweight housing. As in the present example, the weight seat is provided on the one hand on the bearing housing or the rotating arm fixedly connected to the rotating arm, and on the other hand has a weight mounting block 711 as a weight mounting structure, a first weight 721 is provided on the weight mounting block 711, and a second weight 722 is provided on the first weight 721.

In one possible embodiment, the first/second balancing weights are axially movable and/or circumferentially rotatable provided to the first/second balancing weights so as to: the center of gravity of the swing structure including the tension pulley can fall on the second axis by the axial movement and/or rotation of the first/second weight blocks along the first/second weight bars.

Illustratively, the first weight and the second weight are both generally thick cake-like structures and the mounting direction of the two is generally perpendicular. Specifically, the first counterweight rod 731 is a polish rod that is vertically disposed and includes two, the first counterweight rod is movably disposed on the first counterweight rod, and the counterweight mounting block is provided with a telescopic adjusting component (such as an adjusting screw 74) at a position corresponding to the first counterweight rod, so that the first counterweight rod can be pushed to move along the first counterweight rod (in the vertical direction) by making the adjusting screw continuously rise on the basis of abutting the adjusting screw to the lower surface of the first counterweight rod. The second weight bar 732 is a screw or a bar with a threaded section, so that it can be spirally advanced/retreated along the second weight bar (horizontal direction) by rotating the second weight. Based on this, by reasonably adjusting the two balancing weights, it is expected that the center of the entire yaw movement assembly including the tension pulley, the rotating arm, and the bearing housing is located on the tension yaw axis.

It should be understood that the structural form, number, and installation manner of the counterweights on the counterweight base, the movable form that the counterweights can generate, and the structure/mechanism by which the counterweights generate corresponding activities are merely exemplary descriptions, and those skilled in the art can flexibly adjust the counterweights according to actual requirements, and the first counterweights and the second counterweights are respectively and directly arranged on the counterweight installation blocks, the counterweights are in special-shaped structures, and the counterweights comprise a plurality of counterweights greater than two.

Further, in this example, in order to reduce the weight of the weight seat, the weight seat itself is prevented from affecting the center of gravity of the yaw movement assembly including the tension pulley, for example, the weight seat may be subjected to a weight reduction process such as machining the weight reduction groove 712 (or partial thinning). And the weight of the tension swing rod is reduced so as to reduce the mass of the tension arm of the tension wheel when the tension wheel swings.

Based on the above structure, the structural combination related to the first axis in the tension mechanism can be called as a deflection movement assembly, and the deflection movement assembly is mainly responsible for buffering tension change on the diamond wire based on constant torque output by the tension motor. The function of the yaw movement assembly will be described with reference to fig. 9 to 11.

Referring to fig. 9, when the rotation speed of the main roller of the cutting mechanism of the slicer is matched with the rotation speed of the take-up and pay-off roller, the tension swing rod is approximately in the vertical direction, and the tension wheel is at an ideal position. Specifically, in an ideal state, the tension on the diamond wire is constant, and the deflection movement assembly is in a relatively balanced state, so that the tension swing rod cannot swing left and right around the tension deflection axis. Referring to fig. 10, when a moment generated by the tension of the diamond wire is greater than the torque of the tension motor, the diamond wire pulls the tension swing link to swing toward the diamond wire, thereby reducing the tension on the diamond wire by such a swing tendency. As shown in fig. 11, when the torque generated by the tension of the diamond wire is smaller than the torque of the tension motor, the tension motor drives the tension swing rod to swing and rotate towards the direction away from the diamond wire, so that the tension on the diamond wire is increased through the swing trend. Specifically, under the working conditions of diamond wire cutting or high-speed wire running, the tension on the diamond wire changes at any time due to the influence of factors such as servo errors, inertia of the guide wheel, uneven winding and unwinding, resistance of the guide wheel and the like, and in the process, the deflection motion assembly plays a role of absorbing tension fluctuation, for example, when the tension on the diamond wire is larger than the set tension, the deflection motion assembly can be pulled, namely, the tension swing rod is pulled, so that the tension swing rod swings around the tension deflection axis towards the direction of loosening the diamond wire, the degree of 'stretching' of the diamond wire is relieved through the swinging, and the tension increasing trend on the diamond wire is reduced. When the tension on the diamond wire is smaller than the set tension, the tension swing rod swing arm swings towards the direction of stretching the diamond wire under the constant torque output by the tension motor, and the diamond wire can be stretched tightly by the swing, so that the tension defect on the diamond wire is compensated. By this circulation, the tension on the diamond wire can be ensured to be kept in a stable range.

Based on the above structure, the combination of the structures related to the second axis in the tension mechanism can be called a deflection movement assembly, and the deflection movement assembly is mainly used for counteracting the deflection phenomenon generated by the deflection movement of the diamond wire and the related structures along the second axis to a certain extent in the case that the diamond wire deflects in the wire groove of the tension wheel, and therefore reducing or avoiding the wire breakage risk caused by friction between the diamond wire and the wire groove of the tension wheel. The function of the yaw movement assembly is described below with reference to fig. 12 to 13.

Referring to fig. 12, in an ideal state that the diamond wire entering (or leaving) the wire groove of the tension pulley 61 is not deflected, the diamond wire entering the wire groove of the tension pulley from the take-up and pay-off roller 211 (exemplified by the first take-up and pay-off mechanism) is distributed in a vertical direction, and the diamond wire is in a plane in which the wire groove is located. Referring to fig. 13, in the case that the wire entering (or leaving) the wire groove of the tension pulley 61 is deflected (the wire deviates from the plane in which the center of the wire groove of the tension pulley is located), the tension pulley is stressed by the deflection of the wire and thus the tension pulley (and the rotating arm) is deflected by a certain amount about the rotating shaft, based on which the degree of wear between the wire and the wire groove of the tension pulley is reduced and thus the probability of wire breakage or the like is reduced. In addition, the probability of the phenomenon that the diamond wire is out of the wire groove and the like can be effectively reduced based on the deflection. Meanwhile, in the case where the deflection phenomenon has occurred, the degree of deflection may be determined by detecting means such as the ranging sensor 10, for example, by measuring the distance (b-a) between the ranging sensor and the rotating arm 64, as described by the angle and direction of deflection. The distance measured by the distance measuring sensor is a as in the normal state, wherein a is allowed to have a small range of variation. Based on this, the tension pulley is corrected to the ideal position shown in fig. 12 by corresponding correction measures (e.g., by adjusting the winding and unwinding roller in its axial direction, etc.).

It can be seen that, in the tension mechanism of the present utility model, by configuring the tension mechanism with a structure capable of achieving its swinging about the first axis and a structure capable of achieving its deflection about the second axis, it is expected that the operational reliability and cutting quality of the slicer are ensured only by the combination of the take-up and pay-off mechanism, the tension mechanism and the cutting mechanism on the basis of omitting the traverse wheel and the reversing wheel in the conventional slicer of the six-guide wheel structure.

Thus far, the technical solution of the present utility model has been described in connection with the preferred embodiments shown in the drawings, but it is easily understood by those skilled in the art that the scope of protection of the present utility model is not limited to these specific embodiments. Equivalent modifications and substitutions for related technical features may be made by those skilled in the art without departing from the principles of the present utility model, and such modifications and substitutions will fall within the scope of the present utility model.

Claims (28)

1. A tension mechanism is characterized in that the tension mechanism comprises a tension wheel,

In a first aspect, the tension wheel is capable of generating movement about a first axis based at least on torque provided by a drive member;

In a second aspect, at least the tension pulley is movable about a second axis under the influence of an external force;

wherein the first axis and the second axis are not coplanar and have an included angle therebetween.

2. The tension mechanism of claim 1, wherein the tension mechanism comprises a connection assembly,

The tension wheel is connected to the drive member by the connection assembly and thus generates movement about the first axis based on torque provided by the drive member.

3. The tension mechanism of claim 2, wherein the connection assembly comprises a first connection member and a second connection member, the first connection member being coupled to the drive member, the tension wheel being pivotally disposed on the second connection member,

Wherein the first connecting member is rotatably connected with the second connecting member so as to:

The tension wheel is capable of generating a rotational movement about the second axis based at least on the rotational connection.

4. A tension mechanism as recited in claim 3 wherein the first connecting member is formed with an installation space provided with a rotation shaft, and the second connecting member is rotatably connected with the first connecting member through the rotation shaft.

5. A tensioning mechanism according to claim 4, characterized in that the first connecting part comprises a vertical portion which is in driving connection with the drive part on the one hand, which vertical portion on the other hand extends or is provided with a transverse portion which forms the installation space.

6. The tension mechanism as recited in claim 5, wherein the rotation shaft is fixedly disposed at a position of the first connecting portion corresponding to the installation space, and the second connecting member is rotatably connected to the rotation shaft.

7. The tension mechanism of claim 6, wherein the transverse portion comprises a first mounting end and a second mounting end, and wherein the two ends of the shaft are disposed at the first mounting end and the second mounting end, respectively.

8. A tensioning mechanism according to claim 7, wherein the first mounting end and/or the second mounting end is provided with an open structure via which the spindle can enter the mounting space.

9. The tension mechanism of claim 8, wherein the first connecting member comprises a limiting structure, and the rotating shaft is fixedly disposed in the installation space through the limiting structure.

10. The tension mechanism of claim 9, wherein the limit structure is disposed at the first mounting end and/or the second mounting end.

11. The tension mechanism of claim 6, wherein the tension mechanism comprises a bearing housing, the shaft is disposed through the bearing housing, and the second connecting member is fixedly connected to the bearing housing or integrally formed therewith.

12. The tension mechanism of claim 11, wherein the second connecting member comprises a connecting arm, the tension wheel being pivotally mounted to the connecting arm, the connecting arm being fixedly connected to the bearing housing or integrally formed therewith.

13. A tensioning mechanism according to claim 3, wherein the second connecting member is provided with a counterweight assembly.

14. The tension mechanism of claim 13, wherein at least a portion of the weight assembly is a moveable structure.

15. The tension mechanism of claim 14, wherein the weight assembly comprises:

the counterweight block is arranged on the counterweight rod, and the counterweight rod is arranged on the second connecting component in a direct or indirect mode;

Wherein the balancing weight can move along the axial direction of the balancing weight rod and/or around the circumferential direction of the balancing weight rod.

16. The tension mechanism of claim 15, wherein the weight assembly comprises:

an adjusting member capable of applying an external force to the weight lever so as to:

the balancing weight moves along the axial direction of the balancing weight rod under the action of the external force.

17. The tension mechanism of claim 16, wherein the weight bar comprises one or more of; and/or

The adjusting component is an adjusting screw.

18. The tension mechanism of claim 15, wherein the weight is helically movable along the weight rod.

19. The tensioning mechanism of claim 15, wherein the weight comprises at least one of,

Wherein, in the case that the balancing weight includes a plurality of balancing weights, the installation directions of the balancing weight bars corresponding to a plurality of balancing weights are the same or different and/or the balancing weights are directly or indirectly disposed at the second connection part through the balancing weight bars.

20. The tension mechanism of claim 19, wherein the weight comprises a first weight and a second weight, the first weight being disposed on the second connecting member by a weight rod, the second weight being disposed on the first weight by a weight rod,

And an included angle is formed between the counter weight rods corresponding to the first counter weight block and the second counter weight block.

21. A tensioning mechanism as claimed in any one of claims 15 to 20 wherein the second connecting member or structure moving with the second connecting member is provided with a counterweight mount to which the counterweight assembly is provided.

22. A tension mechanism as recited in claim 21 wherein the weight mount is provided with a weight mounting member or a weight mounting structure is formed thereon, the weight assembly being provided to the weight mounting member or the weight mounting structure.

23. A tensioning mechanism according to claim 1, wherein the tensioning wheel has a wire slot around which a cutting wire can be wound, the second axis being in the plane of the wire slot or the second axis being parallel to the plane of the wire slot.

24. The tension mechanism of claim 1, wherein the first axis is perpendicular to the second axis.

25. A wire saw unit, characterized in that it comprises the tension mechanism according to any one of claims 1 to 24.

26. The wire saw unit of claim 25, wherein the wire saw unit comprises a wire take-up and pay-off mechanism and a cutting mechanism, the tension mechanism being disposed between the wire take-up and pay-off mechanism and the cutting mechanism.

27. A wire cutting machine, characterized in that it comprises the tension mechanism of any one of claims 1 to 24; or alternatively

The wire cutting machine comprises the wire saw unit of claim 25 or 26.

28. The wire cutting machine of claim 27, wherein the wire cutting machine is a microtome.