Double helical surface planetary roller screw jacking device

Abstract

A double-helix planetary roller helical pressing device includes a first turntable 10 and a second turntable 20. A conical roller 30 is provided between the first turntable 10 and the second turntable 20. The first turntable has a first conical helical track 11, and the second turntable has a second conical helical track 21. The conical roller has a roller annular groove 31 that meshes with the first conical helical track 11 and the second conical helical track 21. The first turntable 10 and the second turntable 20 rotate coaxially relative to each other, and the conical roller 30 rolls on the first conical helical track 11 and the second conical helical track 21. This invention uses a first turntable with a first conical helical track and a second turntable with a second conical helical track. The conical roller is provided with annular teeth, which allows the conical roller to accurately maintain its radial position, uniformly bear the pressing load, and also avoids slippage between the conical roller and the first and second turntables, improving the operating effect. A roller retainer structure with a roller carriage is used, which can better constrain the posture of the roller during movement.

Description

Technical Field

[0001] This invention pertains to pressure devices, and more particularly to a double-helix planetary roller helical pressure device. Background Technology

[0002] In industrial production, engineering construction, and scientific research, precise fine-tuning of the position of equipment and components is frequently required, and the need to apply top pressure within a small adjustment range is very common. For example, in industrial applications, this involves adjusting the level and clearance of equipment. To improve the performance of heavy-load and precision adjustment of the top-pressure device, Chinese invention patent (application number 2017109060463) discloses a planetary rolling micro-pitch top-pressure device. This device uses planetary threaded rollers with tapered threads. The tapered threads of the planetary threaded rollers contact and roll with the annular toothed grooves of the turntable and top plate, pushing the top plate to make slight ups and downs. This reduces friction during operation, avoids mechanical crawling, and improves the performance of heavy-load and precision adjustment of the top-pressure device. However, due to factors such as operating conditions, there is a possibility of sliding displacement between the tapered threads of the planetary threaded rollers and the turntable and top plate, affecting the accuracy and precision of operation. This device may also produce asynchronous radial movement of multiple planetary threaded rollers, causing them to not bear the pressure load evenly, and even causing the device to lose stability. The above technical solution also uses a roller shaft to connect the planetary thread roller and the cage. When the diameter of the planetary thread roller is small, the diameter of the roller shaft is limited, and its rigidity and strength will be affected. Using a larger diameter planetary thread roller will increase the structural size of the device. Summary of the Invention

[0003] The purpose of this invention is to propose a double-helix planetary roller helical pressing device to improve the structure and performance of planetary rolling pressing devices.

[0004] To achieve the above objectives, the technical solution of the present invention is: a double-helix planetary roller helical pressing device, comprising a first turntable 10 and a second turntable 20, wherein a conical roller 30 is provided between the first turntable 10 and the second turntable 20, the first turntable is provided with a first conical helical track 11, and the second turntable is provided with a second conical helical track 21, wherein the conical roller is provided with a roller annular groove 31 that meshes with the first conical helical track 11 and the second conical helical track 21, the first turntable 10 and the second turntable 20 rotate coaxially relative to each other, and the conical roller 30 rolls on the first conical helical track 11 and the second conical helical track 21.

[0005] Furthermore, a preferred structure of the first turntable, the second turntable, and the conical roller is that the first conical spiral track 11 and the second conical spiral track 21 have the same conical angle α, the first conical spiral track 11 and the second conical spiral track 21 are arranged facing each other, and the conical angle β of the conical roller 30 is adapted to the conical angle α of the first conical spiral track 11 and the second conical spiral track 21.

[0006] Furthermore, in order to meet the motion conditions of the first turntable, the second turntable, and the conical roller, the first conical helical track 11 and the second conical helical track 21 are the same helical track structure. The first conical helical track 11 and the second conical helical track 21 form a vortex shape. The first conical helical track 11 and the second conical helical track 21 are arranged facing each other. The first vortex W1 of the first conical helical track 11 and the second vortex W2 of the second conical helical track 21 form vortices with opposite directions of rotation.

[0007] Furthermore, the first conical spiral track 11 and the second conical spiral track 21 are single-head or multi-head spiral tracks, and the number of conical rollers 30 is one or two times the number of heads of the first conical spiral track or the second conical spiral track. The conical rollers 30 are located at the intersection of the first vortex line W1 and the second vortex line W2 at the WW position.

[0008] Furthermore, a preferred conical spiral track structure is that the cross-sections of the first conical spiral track 11 and the second conical spiral track 21 are triangular, the cross-sectional angle γ1 of the first conical spiral track is symmetrical to the normal 14 of the first conical spiral track, and the cross-sectional angle γ2 of the second conical spiral track is symmetrical to the normal 24 of the second conical spiral track.

[0009] Furthermore, in order to enable the two tapered rollers 30 to move synchronously and maintain a set distance, a roller retainer 40 is provided between the first turntable 10 and the second turntable 20. The roller retainer 40 is provided with a roller groove 41, a roller carriage 42 is provided in the roller groove 41, and the roller carriage is provided with a roller slot 43. The tapered rollers 30 are disposed in the roller slots 43, and the roller carriage 42 moves in the roller grooves 41. The roller carriage 42 moves in a direction perpendicular to the rotation axis of the first turntable and the second turntable.

[0010] Furthermore, in order to make the roller carriage 42 move stably within the roller groove 41, the roller groove 41 of the roller retainer is provided with a carriage guide groove 44, and the roller carriage 42 is provided with a carriage guide rail 45, the carriage guide rail 45 slidingly engaging with the carriage guide groove 44.

[0011] Furthermore, in order to prevent the roller groove 41 from dislodging from the roller retainer 40, a retainer ring 46 is provided on the outer diameter of the roller retainer 40.

[0012] The beneficial effects of this invention are as follows: The use of a first turntable with a first conical spiral track and a second turntable with a second conical spiral track, along with an annular groove on the conical rollers, avoids asynchronous radial movement of multiple conical rollers, ensuring accurate radial positioning of the conical rollers and uniform bearing of top pressure loads. It also prevents slippage between the conical rollers and the first and second turntables, improving operational efficiency. Furthermore, the use of a roller cage structure with a roller carriage allows for better constraint of the rollers' posture during movement, keeping the roller axis pointing towards the turntable's rotation axis and preventing roller swaying. The diameter of the conical rollers is not limited by the cage mechanism, thus optimizing the structural design of the conical rollers.

[0013] The present invention will now be described in detail with reference to the accompanying drawings and embodiments. Attached Figure Description

[0014] Figure 1 This is a structural diagram of the present invention. The first conical spiral track and the second conical spiral track are single-head spiral tracks.

[0015] Figure 2 This is a structural diagram of the present invention, which hides the second turntable and the cage ring;

[0016] Figure 3 This is an exploded view of the structure of the present invention;

[0017] Figure 4 This is a cross-sectional view of the first turntable, the second turntable, and the conical roller of the present invention;

[0018] Figure 5 This is a distribution diagram of the conical rollers of the present invention on the helical track of the first conical surface;

[0019] Figure 6 This is a schematic diagram of the motion state of the present invention;

[0020] Figure 7 This is a schematic diagram of the first conical spiral track and the second conical spiral track of the present invention being arranged face to face, with the first vortex line W1 and the second vortex line W2 forming vortex lines with opposite directions of rotation.

[0021] Figure 8 This is a schematic diagram of the circular movement of the intersection line WW of the first vortex line W1 and the second vortex line W2 of the present invention.

[0022] Figure 9 This is a structural diagram of the present invention, which uses a first conical spiral track and a second conical spiral track with a recessed center;

[0023] Figure 10This is a structural diagram of the present invention, showing that the roller slide groove is provided with a slide guide groove and the roller slide is provided with a slide guide rail;

[0024] Figure 11 This is an exploded view of the structure of the present invention. The first conical spiral track and the second conical spiral track are double-headed spiral tracks.

[0025] Figure 12 This invention uses a double-headed spiral track for both the first and second conical spiral tracks, and the distribution diagram of the conical rollers on the first conical spiral track is shown.

[0026] Figure 13 The first and second conical spiral tracks of this invention are double-headed spiral tracks. The first and second conical spiral tracks are arranged facing each other. The first vortex W1 and the second vortex W2 form vortexes with opposite directions of rotation.

[0027] Figure 14 This is a schematic diagram of the circular movement of the intersection line WW of the first conical spiral track and the second conical spiral track of the present invention, which adopts a double-headed spiral track.

[0028] Figure 15 This is an exploded view of the structure of the present invention. The first conical spiral track and the second conical spiral track are three-headed spiral tracks.

[0029] Figure 16 This invention uses a three-headed helical track for both the first and second conical helical tracks, and the distribution diagram of the conical rollers on the first conical helical track is shown.

[0030] Figure 17 The first and second conical spiral tracks of this invention are three-headed spiral tracks. The first and second conical spiral tracks are arranged facing each other, and the first vortex W1 and the second vortex W2 form vortexes with opposite directions of rotation. Detailed Implementation

[0031] Example 1:

[0032] like Figures 1 to 8 A double-helix planetary roller helical pressing device includes a first turntable 10 and a second turntable 20, with a conical roller 30 disposed between the first turntable 10 and the second turntable 20. The first turntable 10 and the second turntable 20 are provided with a common axis C.

[0033] The outer end face 12 of the first turntable 10 is a plane perpendicular to the axis C. The inner end face of the first turntable 10 is provided with a first conical spiral track 11, which gradually rises from the outside to the inside, forming a conical tooth surface on the inner end face of the first turntable 10. The first conical spiral track 11 has a vortex shape in the end face direction, which can be defined as the first vortex W1. The cross-section of the first conical spiral track 11 is triangular.

[0034] The outer end face 22 of the second turntable 20 is a plane perpendicular to the axis C. The inner end face of the second turntable 20 is provided with a second conical spiral track 21, which gradually rises from the outside to the inside, forming a conical tooth surface on the inner end face of the second turntable 20. The second conical spiral track 21 has a vortex shape in the end face direction, which can be defined as a second vortex W2. The cross-section of the second conical spiral track 21 is triangular.

[0035] like Figure 4 As shown, the first conical spiral track 11 and the second conical spiral track 21 have the same spiral track structure, with the same cone angle α, triangular cross-sections, and the same track gauge P. Viewing the first conical spiral track 11 from direction F1 towards the first conical spiral track 11 and the second conical spiral track 21 from direction F2 towards the second conical spiral track 21, the first conical spiral track 11 and the second conical spiral track 21 have a vortex shape with the same direction of rotation; that is, the first vortex W1 and the second vortex W2 are the same, including the same track gauge P and the same direction of rotation. Figure 4 As shown, the section angle γ1 of the first conical spiral track is symmetrical about the normal 14 of the first conical spiral track, and the section angle γ2 of the second conical spiral track is symmetrical about the normal 24 of the second conical spiral track. The angle between the normal 14 of the first conical spiral track and the rotation axis C is 90° - α / 2; similarly, the angle between the normal 24 of the second conical spiral track and the rotation axis C is 90° - α / 2.

[0036] In this embodiment, the first vortex line W1 and the second vortex line W2 are single-headed vortex lines.

[0037] In the assembled structure, the first conical spiral track 11 and the second conical spiral track 21 are arranged facing each other. Viewed along axis C, the first vortex line W1 of the first conical spiral track 11 and the second vortex line W2 of the second conical spiral track 21 form vortices with opposite directions of rotation. The first vortex line W1 and the second vortex line W2 have two intersecting lines WW that are symmetrically arranged in the circumferential direction, as shown below. Figure 7 As shown.

[0038] A conical roller 30 is provided between the first turntable 10 and the second turntable 20. The cone angle β of the conical roller 30 is adapted to the cone angle α of the first conical spiral track 11 and the second conical spiral track 21, i.e., α+β=180°. The conical roller is provided with a roller annular groove 31 that meshes with the first conical spiral track 11 and the second conical spiral track 21. The number of conical rollers 30 is one or two times the number of heads of the first or second conical spiral track. In this embodiment, the first vortex line W1 and the second vortex line W2 are single-head vortex lines. The first and second conical spiral tracks have one head, and two conical rollers 30 are respectively located at the two intersection lines WW of the first vortex line W1 and the second vortex line W2.

[0039] The two conical rollers are positioned differently in the first turntable 10 and the second turntable 20, and the positions of their corresponding spiral tracks with vortex structures differ by half a track gauge P. To ensure that the outer end faces of the first turntable 10 and the second turntable 20 are parallel, and that the two conical rollers mesh with the spiral tracks of the first and second turntables, in this embodiment, the outer diameters of the two conical rollers are different. For example... Figure 5 As shown, the two tapered rollers are labeled 3a and 3b, with diameters of their large ends of da and db, respectively. Tapered roller 3a is positioned relatively far from the axis C. Tapered roller 3b is closer to the axis C than tapered roller 3a. In fact, the positions of tapered roller 3b and tapered roller 3a differ by half a track gauge P, and the diameter db of the large end of tapered roller 3b is smaller than the diameter da of the large end of tapered roller 3a. Alternatively, the position of the roller annular groove 31 of the tapered roller can be changed to achieve the same technical effect.

[0040] The first turntable 10 and the second turntable 20 rotate coaxially relative to each other, and the conical roller 30 rolls on the first conical helical track 11 and the second conical helical track 21. Based on the rolling motion principle of the conical helical track and the annular groove meshing structure of the conical roller, the circumferential rolling stroke (angular stroke) of the conical roller 30 is half the relative rotation stroke (angular stroke) of the first turntable 10 and the second turntable 20, and the circumferential movement stroke of the two intersecting lines WW of the first spiral line W1 and the second spiral line W2 is half the relative rotation stroke of the first spiral line W1 and the second spiral line W2. For example... Figure 7 , Figure 8 As shown, when the relative rotational stroke of the first spiral line W1 and the second spiral line W2 is θ1 = 90° (in the illustration, the first spiral line W1 rotates 90° while the second spiral line W2 remains stationary), the relative rotational stroke of the intersection line WW of the first spiral line W1 and the second spiral line W2 is θ2 = 45°, thus keeping the conical roller 30 at the position of the intersection line WW during movement. Therefore, the rolling of the conical roller 30 can be perfectly matched with the relative rotational relationship between the first turntable 10 and the second turntable 20.

[0041] The first turntable 10 has a central shaft 13 at its center, and the second turntable has a central hole 23 that rotatably engages with the central shaft 13. The first turntable 10 and the second turntable 20 rotate coaxially relative to each other. As a spiral pressing device, the outer end face 12 of the first turntable and the outer end face 22 of the second turntable bear pressure, and the conical roller 30 is subjected to the pressure of the first turntable and the second turntable. When the first turntable 10 and the second turntable 20 rotate relative to each other, the conical roller 30 rolls on the first conical spiral track 11 and the second conical spiral track 21, and performs planetary motion around the center of the first turntable 10 and the second turntable 20. When the conical roller 30 rolls, it moves along the first conical helical track 11 and the second conical helical track 21, that is, along the vortex line. The first conical helical track 11 and the second conical helical track 21, through their meshing relationship, push the conical roller 30 to move, producing a displacement close to or away from the rotating shaft C. When the conical roller 30 moves towards the rotating shaft C, under the action of the conical angle α, it pushes the first turntable 10 and the second turntable 20 to separate axially. Figure 6 As shown, the tapered roller 30 can push the second turntable 20 upward to achieve the pressing function. Conversely, when the tapered roller 30 moves away from the rotation axis, the second turntable 20 falls back towards the first turntable 10, thus resetting the pressing device.

[0042] To ensure that the two tapered rollers 30 move synchronously and maintain a set distance, a roller retainer 40 is provided between the first turntable 10 and the second turntable 20. The roller retainer 40 has two roller grooves 41, the direction of which is perpendicular to the rotation axis C of the first turntable and the second turntable.

[0043] A roller carriage 42 is provided within the roller groove 41. The roller carriage 42 moves along the roller groove. The roller carriage has a roller groove 43, the size of which is adapted to the conical roller 30. In this embodiment, the roller grooves 43 of the two roller grooves are respectively adapted to the two conical rollers (3a, 3b). The conical rollers 30 are disposed within the roller grooves 43, so that the conical rollers can only roll within the roller grooves 43. The axis of the conical roller 30 intersects the axis C perpendicularly. When the conical roller 30 moves closer to or away from the axis of rotation, it pushes the roller carriage 42 to move within the roller groove 41. The roller carriage 42 moves in a direction perpendicular to the axis C. The roller carriage 42 keeps the two conical rollers 30 (3a, 3b) synchronized during planetary motion.

[0044] To prevent the roller groove 41 from dislodging from the roller cage 40, a cage ring 46 is provided on the outer diameter of the roller cage 40.

[0045] In this embodiment, the first turntable 10 is positioned below the second turntable 20. Alternatively, the first turntable 10 can be positioned above the second turntable 20 to achieve the same technical effect.

[0046] In this embodiment, the first turntable 10 is provided with a central shaft 13 and the second turntable is provided with a central hole 23. Similarly, the second turntable can be provided with a central shaft and the first turntable can be provided with a central hole to achieve the same technical effect.

[0047] In the prior art (patent application number 2017109060463), planetary threaded rollers are provided with tapered threads, and the turntable and top plate are provided with annular toothed grooves. Each planetary threaded roller can generate radial displacement (i.e., movement towards the rotation axis of the turntable) during its rotation. During the repeated movement of the planetary threaded rollers, it is difficult to ensure that the multiple planetary threaded rollers rotate completely synchronously. This may result in asynchronous radial movement of multiple planetary threaded rollers, preventing them from maintaining uniform contact with the turntable and top plate. Consequently, the multiple planetary threaded rollers cannot bear the pressure load evenly, and the device may lose stability. To overcome this technical problem, the prior art uses a structure with synchronous toothed discs on the turntable and top plate and synchronous gears on the planetary threaded rollers. On the one hand, this increases the structural complexity and manufacturing cost of the device. On the other hand, since the planetary threaded rollers will generate radial movement relative to the turntable and top plate (equivalent to the first turntable 10 and the second turntable 20 in this invention) during the movement of the device, it is difficult for the toothed discs and gears to maintain good meshing and transmission effects, which also makes it difficult to ensure accurate synchronous movement of multiple planetary threaded rollers.

[0048] In the structure of this invention, the first turntable 10 is provided with a first conical helical track 11, the second turntable 20 is provided with a second conical helical track 21, and the conical rollers are provided with roller annular grooves 31, which mesh with the first conical helical track 11 and the second conical helical track 21. The rotation of the conical rollers does not cause radial displacement (i.e., displacement toward axis C). Radial displacement only occurs when the conical rollers roll (planetary motion) along the first and second conical helical tracks. The position of the conical rollers on the first and second conical helical tracks determines the position of their radial displacement. Since the roller retainer 40 defines the relative positions of each conical roller, multiple conical rollers (equivalent to planetary thread rollers in the prior art) can maintain synchronous radial displacement.

[0049] In the prior art, when certain factors prevent the planetary thread rollers from rolling smoothly, the turntable or top plate will slide relative to the planetary thread rollers, causing the pressing device to lose its lifting function and affecting the accurate operation of the device.

[0050] In this invention, the roller annular groove 31 meshes with the first conical spiral track 11 and the second conical spiral track 21. The first conical spiral track 11 and the second conical spiral track 21 are spiral structures with vortex lines, which avoids slippage between the conical roller 30 and the first conical spiral track 11 or the second conical spiral track 21. The relative rotation of the first turntable and the second turntable can force the conical roller to move along the conical spiral track.

[0051] In the prior art, planetary threaded rollers are equipped with roller shafts, and the planetary threaded rollers are mounted on planetary roller cages via the roller shafts. This structure requires the planetary roller cage to have sufficient thickness to accommodate the roller shafts, which increases the overall axial dimension of the device. The present invention uses a roller cage 40 with roller carriages 42, which allows the roller cage to have a minimal thickness, making the device structure more compact.

[0052] Planetary roller screw jacking devices possess excellent mechanical properties. Double-helix planetary roller screw jacking devices are characterized by high precision, with roller diameters and thread tolerances precisely machined and controlled to achieve high-precision motion and positioning. Double-helix planetary roller screw jacking devices are characterized by long service life, exhibiting excellent wear resistance and fatigue resistance, maintaining stable performance even in harsh working environments, reducing the frequency of maintenance and replacement. Double-helix planetary roller screw jacking devices are characterized by low friction, with a very low coefficient of friction, reducing energy loss and heat generation, thereby improving the efficiency and stability of the mechanical system. During transmission, the rollers in a double-helix planetary roller screw jacking device primarily bear the radial pressure, while the meshing threads and annular grooves bear the component force along the conical surface. Therefore, they have better load-bearing capacity and stronger impact resistance, meeting the requirements of ultra-high load and high speed applications. Their load-bearing capacity is far superior to common planetary roller screw structures because the threads of planetary roller screws bear the entire axial external load force. The double-helix planetary roller helical pressing device is highly adaptable, and its structural design and parameter selection can be adapted to different application scenarios and mechanical system requirements. For example, for some special occasions requiring high-precision positioning, the double-helix planetary roller helical pressing device can meet these requirements through special design and manufacturing. It is particularly suitable for applications requiring ultra-high load, high precision, low friction, low torque, and long service life in confined spaces such as narrow, circular, and high-height areas.

[0053] Example 2:

[0054] like Figure 9 A double-helix planetary roller helical pressing device, this embodiment is a structural replacement of embodiment one.

[0055] In Embodiment 1, the first conical spiral track 11 and the second conical spiral track 21 are conical structures with a centrally convex shape, and the small-diameter end of the conical roller 30 faces the rotation center. In this embodiment, the first conical spiral track 11 and the second conical spiral track 21 are concave conical structures, and the large-diameter end of the conical roller 30 faces the rotation center, achieving the same technical effect.

[0056] As a further option, the first conical spiral track 11 and the second conical spiral track 21 can be used with different conical angles α.

[0057] Example 3:

[0058] like Figure 10 A double-helix planetary roller helical pressing device, this embodiment is an improvement of embodiment one.

[0059] In this embodiment, in order to make the roller carriage 42 move stably within the roller groove 41, the roller groove 41 of the roller retainer is provided with a carriage guide groove 44, and the roller carriage 42 is provided with a carriage guide rail 45, which slides in cooperation with the carriage guide groove 44.

[0060] Example 4:

[0061] like Figures 11 to 14 A double-helix planetary roller helical pressing device, this embodiment is an improvement of embodiment one.

[0062] Example 1 is a basic double-helix planetary roller helical pressing device. The first conical helical track 11 and the second conical helical track 21 are single-head helical tracks, and at most two conical rollers 30 can be set. However, the two conical rollers 30 alone cannot make the first turntable 10 and the second turntable 20 have a stable combined structure. It is necessary to rely on the cooperation of the central shaft to maintain the combined structure of the first turntable 10 and the second turntable 20, and its load-bearing capacity is also limited.

[0063] In this embodiment, the first conical spiral track 11 and the second conical spiral track 21 are double-headed spiral tracks. Since the number of conical rollers 30 is one or two times the number of heads of the first or second conical spiral track, this embodiment has four conical rollers 30.

[0064] Similarly, both the first spiral line W1 and the second spiral line W2 are double-headed spiral lines, and the first spiral line W1 and the second spiral line W2 have four intersecting lines WW. Four conical rollers 30 are respectively set at the four intersecting lines WW.

[0065] To ensure the symmetrical structure of the first turntable 10 and the second turntable 20, the four conical rollers have different outer diameters. For example... Figure 12As shown, the four conical rollers are labeled 3a, 3b, 3c, and 3d. Conical rollers 3a and 3c are the same size and symmetrically arranged around axis C. Conical rollers 3b and 3d are also the same size and symmetrically arranged around axis C. The large end diameter d1 of conical rollers 3a and 3c is larger than the large end diameter d2 of conical rollers 3b and 3d. Conical rollers 3a and 3c are located relatively far from axis C. Conical rollers 3b and 3d are closer to axis C than conical rollers 3a and 3c. In fact, the positions of conical rollers 3b and 3d differ from those of conical rollers 3a and 3c by half a track gauge P.

[0066] The first turntable 10 and the second turntable 20 rotate coaxially relative to each other, and the conical roller 30 rolls on the first conical helical track 11 and the second conical helical track 21. Based on the rolling motion principle of the conical helical track and the annular groove meshing structure of the conical roller, the circumferential rolling stroke (angular stroke) of the conical roller 30 is half the relative rotation stroke (angular stroke) of the first turntable 10 and the second turntable 20, and the circumferential movement stroke of the four intersecting lines WW of the first spiral line W1 and the second spiral line W2 is also half the relative rotation stroke of the first spiral line W1 and the second spiral line W2. For example... Figure 13 , Figure 14 As shown, when the relative rotational stroke of the first spiral line W1 (double-headed spiral line) and the second spiral line W2 (double-headed spiral line) is 90° (in the diagram, the first spiral line W1 rotates 90° while the second spiral line W2 remains stationary), the relative rotational stroke of the intersection line WW of the first spiral line W1 and the second spiral line W2 is 45°. Therefore, the rolling of the conical roller 30 and the relative rotational relationship between the first turntable 10 and the second turntable 20 can be perfectly matched.

[0067] In this embodiment, the first conical helical track 11 and the second conical helical track 21 adopt a double-headed helical track, which can be equipped with four conical rollers 30, significantly improving the load-bearing capacity of the double-helical planetary roller helical pressing device. The four conical rollers 30 themselves also enable the first turntable 10 and the second turntable 20 to have a stable combined structure.

[0068] Example 5:

[0069] like Figures 15 to 17 A double-helix planetary roller helical pressing device, this embodiment is a further improvement of embodiment one.

[0070] In this embodiment, the first conical spiral track 11 and the second conical spiral track 21 are three-head spiral tracks. Since the number of conical rollers 30 is one or two times the number of heads of the first or second conical spiral track, this embodiment has six conical rollers 30.

[0071] Similarly, both the first spiral line W1 and the second spiral line W2 are three-headed spiral lines, and the first spiral line W1 and the second spiral line W2 have six intersecting lines WW, such as... Figure 17 As shown. Six tapered rollers 30 are respectively positioned at the six intersecting lines WW, as follows. Figure 16 As shown.

[0072] To ensure the symmetrical structure of the first turntable 10 and the second turntable 20, the outer diameters of the six tapered rollers are different. For example... Figure 16 As shown, the six conical rollers are labeled 3a, 3b, 3c, 3d, 3e, and 3f. Conical rollers 3a, 3c, and 3e are of the same size, as are conical rollers 3b, 3d, and 3f. The conical rollers 3a, 3c, and 3e are circumferentially staggered with those 3b, 3d, and 3f. The large-end diameter d3 of conical rollers 3a, 3c, and 3e is larger than the large-end diameter d4 of conical rollers 3b, 3d, and 3f. Conical rollers 3a, 3c, and 3e are positioned relatively far from the axis C; conical rollers 3b, 3d, and 3f are closer to the axis C than conical rollers 3a, 3c, and 3e. In fact, the positions of conical rollers 3a, 3c, and 3e differ from those of conical rollers 3b, 3d, and 3f by half a track gauge P.

[0073] Similar to Embodiments 1 and 2, the rolling of the six conical rollers 30 and their relative rotation to the first turntable 10 and the second turntable 20 can be perfectly matched.

[0074] In this embodiment, the first conical spiral track 11 and the second conical spiral track 21 adopt a three-head spiral track, which can be equipped with six conical rollers 30. That is, the number of conical rollers 30 is twice the number of heads of the first conical spiral track or the second conical spiral track, which can further improve the load-bearing capacity of the double-helix planetary roller spiral pressing device.

[0075] Similarly, three tapered rollers 30 can be set, meaning the number of tapered rollers 30 is twice the number of heads of the first or second tapered helical track. For example, setting tapered rollers 3a, 3c, and 3e can achieve stable three-point support.

[0076] Furthermore, according to the case descriptions of Embodiments 1, 4, and 5, a double-helix planetary roller helical pressing device can, depending on factors such as space and force, have more helical tracks (first conical helical track 11 and second conical helical track 21) with a greater number of heads, paired with conical rollers having one or two times the number of heads of the helical tracks. When the number of conical rollers 30 is one times the number of heads of the first or second conical helical track, the conical rollers are of the same specification and are evenly distributed around the rotation center circumference. When the number of conical rollers 30 is twice the number of heads of the first or second conical helical track, two different specifications of conical rollers are used. Conical rollers of the same specification are evenly distributed around the rotation center circumference, while conical rollers of different specifications are staggered.

[0077] The first conical spiral track 11 and the second conical spiral track 21 can also adopt other cross-sectional structures, including but not limited to trapezoidal cross-section, rectangular cross-section, sawtooth cross-section, semi-circular cross-section and other cross-sectional shapes.

Claims

1. A double-helix planetary roller helical pressing device, characterized in that, The device includes a first turntable (10) and a second turntable (20). A conical roller (30) is provided between the first turntable (10) and the second turntable (20). The first turntable is provided with a first conical spiral track (11), and the second turntable is provided with a second conical spiral track (21). The conical roller is provided with a roller annular groove (31) that meshes with the first conical spiral track (11) and the second conical spiral track (21). The first turntable (10) and the second turntable (20) rotate coaxially relative to each other, and the conical roller (30) rolls on the first conical spiral track (11) and the second conical spiral track (21).

2. The double-helix planetary roller helical pressing device according to claim 1, characterized in that, The first conical spiral track (11) and the second conical spiral track (21) have the same conical angle (α). The first conical spiral track (11) and the second conical spiral track (21) are arranged face to face. The conical angle (β) of the conical roller (30) is adapted to the conical angle (α) of the first conical spiral track (11) and the second conical spiral track (21).

3. The double-helix planetary roller helical pressing device according to claim 1, characterized in that, The first conical spiral track (11) and the second conical spiral track (21) have the same spiral track structure. The first conical spiral track (11) and the second conical spiral track (21) form a vortex shape. The first conical spiral track (11) and the second conical spiral track (21) are arranged facing each other. The first vortex (W1) of the first conical spiral track (11) and the second vortex (W2) of the second conical spiral track (21) form vortices with opposite directions of rotation.

4. The double-helix planetary roller helical pressing device according to claim 3, characterized in that, The first conical spiral track (11) and the second conical spiral track (21) are single-head or multi-head spiral tracks. The number of conical rollers (30) is one or two times the number of heads of the first conical spiral track or the second conical spiral track. The conical rollers (30) are located at the intersection (WW) of the first vortex line (W1) and the second vortex line (W2).

5. The double-helix planetary roller helical pressing device according to claim 1, characterized in that, The cross-sections of the first conical spiral track (11) and the second conical spiral track (21) are triangular. The cross-sectional angle of the first conical spiral track is symmetrical to the normal of the first conical spiral track, and the cross-sectional angle of the second conical spiral track is symmetrical to the normal of the second conical spiral track.

6. The double-helix planetary roller helical pressing device according to claim 1, characterized in that, A roller retainer (40) is provided between the first turntable (10) and the second turntable (20). The roller retainer (40) is provided with a roller groove (41). A roller carriage (42) is provided in the roller groove (41). The roller carriage is provided with a roller groove (43). The conical roller (30) is disposed in the roller groove (43). The roller carriage (42) moves in the roller groove (41). The roller carriage (42) moves in a direction perpendicular to the rotation axis of the first turntable and the second turntable.

7. The double-helix planetary roller helical pressing device according to claim 6, characterized in that, The roller retainer has a roller groove (41) with a carriage guide groove (44), and the roller carriage (42) has a carriage guide rail (45). The carriage guide rail (45) slides in cooperation with the carriage guide groove (44).

8. The double-helix planetary roller helical pressing device according to claim 6, characterized in that, The outer diameter of the roller retainer (40) is provided with a retainer ring (46).

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