Reverse transition groove planetary roller screw

Abstract

The application discloses a reverse type transition groove row planetary roller screw, which comprises a screw rod, a plurality of first annular grooves are arranged on the outer wall of the screw rod and are parallel to the axial direction of the screw rod, the plurality of first annular grooves are divided into a plurality of annular groove groups, and the spacing between adjacent annular groove groups is d; a nut is coaxially arranged on the outer wall of the screw rod; a plurality of rollers are annularly arranged between the screw rod and the nut, the plurality of rollers are installed on the outer wall of the screw rod through a planet carrier, the axial direction of the rollers is parallel to the axial direction of the screw rod, each roller is provided with a transmission section, the transmission section is provided with a plurality of second annular grooves which are parallel to each other, the transmission section of each roller is oppositely arranged with one annular groove group, and the rollers are meshed with the nut and the screw rod through the transmission sections. The annular grooves of the rollers are matched with the annular grooves of the screw rod, the annular grooves of the rollers are matched with the threads of the nut, and the spacing between the plurality of annular grooves on the screw rod is offset, so that the planetary roller screw is not self-locked and runs at a constant lead.

Description

Technical Field

[0001] This invention relates to the field of transmission devices, specifically to ball screws, and more particularly to reverse-type transition grooved planetary ball screws. Background Technology

[0002] Planetary roller screws, as key transmission mechanisms for converting helical motion into linear motion, transmit power through the helical meshing of the screw, rollers, and nut, offering advantages such as high load capacity, long lifespan, and wide speed range. Among various configurations, the reverse-type planetary roller screw, with its internal screw and long nut enclosure, has a particularly compact radial structure, making it especially suitable for space-constrained precision applications, such as robot joints or braking systems in new energy vehicles.

[0003] However, existing reverse planetary roller screw pairs cannot meet the following comprehensive requirements: high load capacity, balance between small and medium lead, constant lead, non-self-locking motion transmission, and high-precision, large-scale, and low-cost mass production.

[0004] Traditional reverse-type planetary roller screws, such as the RVI series in the Swiss Rollvis catalog, have a minimum practical lead of 1.5mm, a constant lead, reverse motion transmission without self-locking, high load capacity, high DN value, and can handle high-speed input. However, because the rollers are a combination of external gears and external threads, and the screw is also a combination of external gears and external threads, manufacturing is difficult and costly, making mass production challenging. When the lead is less than 1mm, the nut diameter is large, limiting its application range. It cannot be used in fields such as smaller dexterity hands.

[0005] Patent application CN120426368A discloses a reverse-type toothless planetary roller screw, comprising a screw, a long nut, a planetary carrier assembly, and multiple rollers. It features reverse motion transmission without self-locking, high load capacity, high DN value, and high-speed input capability. While its manufacturing difficulty is lower than traditional reverse-type planetary roller screws, and its cost is slightly lower, large-scale production is challenging. When the lead is less than 1mm, the nut diameter is large, limiting its application range. It also cannot be used in fields such as smaller, dexterous hands.

[0006] Patent CN104675946B discloses a differential planetary roller screw (reverse differential planetary roller screw) with a stepped, threadless annular groove structure for the rollers, and a corresponding stepped, threadless annular groove structure for both the screw and rollers. It boasts high load capacity, high DN value, and high-speed input capability, with a small lead (as small as 0.2mm), enabling large-scale, low-cost mass production. However, the lead is not constant, requiring closed-loop control with a displacement sensor, significantly limiting its application. This type of product has a self-locking characteristic and cannot reverse transmission. Reverse transmission and non-self-locking are required in mainstream applications. Summary of the Invention

[0007] The technical problem this invention aims to solve is to achieve a balance between high load capacity, small and medium lead lengths, constant lead length, non-self-locking motion transmission, high precision, large-scale production, and low cost. This invention provides a reverse-type transition slot planetary roller screw.

[0008] The technical solution adopted by this invention to solve its technical problem is: a reverse-type jump-slot planetary roller screw, comprising:

[0009] The lead screw has a plurality of parallel first annular grooves on its outer side wall along its axial direction. The plurality of first annular grooves are divided into multiple annular groove groups, and the distance between adjacent annular groove groups is d.

[0010] Nut, which is coaxially sleeved on the outside of the lead screw;

[0011] Multiple rollers are arranged in a ring between the lead screw and the nut. The rollers are mounted on the outer wall of the lead screw via a planetary carrier. The axial direction of the rollers is parallel to that of the lead screw. Each roller has a transmission section with parallel second annular grooves. The transmission section on each roller is opposite to a group of annular grooves. The pitch of the nut, the groove distance between adjacent first annular grooves in the same annular groove group, and the groove distance between adjacent second annular grooves are all equal. The rollers mesh with the nut and the lead screw through the transmission sections.

[0012] This invention relates to a reverse-gap planetary roller screw, which, through the cooperation of the screw, nut, and multiple rollers, and the engagement of the annular groove group on the screw with the roller transmission section, achieves axial positioning and transmission of the rollers. The rollers, through the simultaneous meshing of the transmission section with the nut and screw, and the setting of the spacing between adjacent annular groove groups, realize planetary motion of the rollers between the screw and nut. This converts the rotational motion of the screw into the axial movement of the nut, or vice versa. The overall structure is simple, and the transmission relationship is clear. Each roller in this structure only requires machining a small section of annular groove, completely eliminating the precision machining bottleneck of traditional roller composite structures (gear and thread structures), reducing manufacturing difficulty and production costs, and decreasing vibration and noise during operation of the linear actuation mechanism. The spacing design of the annular groove group on the screw allows for a stable arrangement of at least three rollers even on a single-start screw, achieving smooth, non-locking, constant lead transmission, and even small lead motions from 0.2mm to 1mm.

[0013] Furthermore, the number of heads in the nut is n, and the plurality of rollers includes n reference rollers and 0 or more auxiliary rollers, with the n reference rollers meshing with the same annular groove group.

[0014] By adopting the above technical solution, the reference roller plays a phase positioning role in the transmission, and the auxiliary roller can be flexibly configured as needed, thereby optimizing the number of rollers and reducing manufacturing costs while ensuring the transmission function.

[0015] Furthermore, n reference rollers are evenly distributed around the outer periphery of the lead screw, and the included angle between adjacent reference rollers is β=360° / n.

[0016] Furthermore, the area between adjacent reference rollers is the design interval, and the annular groove group opposite the transmission section on the reference roller is the reference groove group. Taking the reference groove group as the 0th annular groove group, the distance between the i-th annular groove group and the (i-1)-th annular groove group along the axial direction of the lead screw is... Where M is the pitch of the nut. Let k be the angle between the auxiliary roller corresponding to the k-th annular groove group and a reference roller at the end of its design interval, where k = i or i-1.

[0017] By adopting the above technical solution, defining the design interval and the reference groove group, and giving the calculation formula for the distance d between adjacent ring groove groups, the axial position of each ring groove group can be accurately determined according to the nut pitch and the roller phase angle, thereby realizing precise segmented displacement control in the nut axial direction, and providing a mathematical basis for the design of the planetary roller screw.

[0018] Furthermore, the total number of rollers is at least three, and among the multiple rollers, at least three rollers are solid.

[0019] By adopting the above technical solution, under the condition that the total number of rollers is greater than or equal to three, the number of appropriate reference rollers or auxiliary rollers can be reduced, so that only a small number of physical rollers need to be arranged in the actual structure to meet the transmission requirements. The concept of virtual rollers simplifies kinematic analysis and parameter design and reduces structural complexity.

[0020] Furthermore, the multiple rollers are circumferentially distributed around the outer periphery of the lead screw.

[0021] By adopting the above technical solution, each roller is evenly distributed in the circumferential direction, the force is balanced, the transmission is smooth, and the uneven distribution of rollers is avoided, thus avoiding uneven load and vibration.

[0022] Furthermore, a limiting element is provided on the lead screw, which is used to limit the axial sliding of the planetary carrier.

[0023] Furthermore, the limiting member is provided in two locations at both ends of the planetary carrier, and the lead screw is provided with a groove for embedding the limiting member.

[0024] By adopting the above technical solution, the axial slippage of the planetary carrier is restricted by setting a limiting component on the lead screw, which effectively prevents the planetary carrier from moving axially during operation, ensures the precise meshing position between the rollers, nut, and lead screw, and improves the stability and repeatability of the transmission.

[0025] Furthermore, the planetary carrier has a circular hole at its end for inserting the end of the roller.

[0026] By adopting the above technical solution, and by setting a circular hole at the end of the planetary carrier for the roller end to be inserted, the end of the roller can be accurately positioned, ensuring the axial parallelism and circumferential distribution accuracy of the roller. At the same time, the circular hole structure is simple and easy to process, reducing the manufacturing cost of the planetary carrier.

[0027] Furthermore, the end of the roller is provided as a connecting section, and a stepped surface is provided between the connecting section and the roller body facing the connecting section. When the connecting section is inserted into the circular hole, the stepped surface abuts against the end of the planetary carrier.

[0028] By adopting the above technical solution and setting the stepped surface, the axial relative position between the roller and the planetary carrier is further limited, reducing the possibility of axial movement of the roller within the planetary carrier.

[0029] The beneficial effects of this invention are:

[0030] 1. The reverse-type jump-slot planetary roller screw of the present invention, through the rigid constraint of the planetary carrier on the rollers, ensures that the rollers can only rotate around their own axis when the screw rotates, and the planetary carrier drives the rollers to revolve when the screw and nut slide relative to each other. Multiple annular grooves distributed axially on the surface of the rollers form a mating interface with the corresponding annular grooves on the outer side of the screw. When the rollers rotate, the inclined surface or curved profile of the sidewall of the annular grooves interacts with the annular grooves of the screw, forcing the screw and rollers to move together axially.

[0031] By offsetting the spacing of the ring grooves on the lead screw, this structure allows for axial movement between the lead screw and the nut using at least three rollers. Simultaneously, this structure eliminates the traditional threaded engagement structure, simplifying the ring groove machining and eliminating the need to consider helix angle matching, enabling smooth transmission even on single-ended nuts. This structure significantly reduces the manufacturing difficulty of the rollers and lead screw, ensuring smooth transmission and repeatable positioning accuracy. Compared to ball screws, it can withstand greater loads, enabling a stable arrangement of at least three rollers even on conventional single-ended nuts, providing precision micro-feed capability. This offers a simplified and cost-effective solution for applications requiring non-self-locking, constant lead movement. Attached Figure Description

[0032] The present invention will be further described below with reference to the accompanying drawings and embodiments.

[0033] Figure 1 This is a schematic diagram of the reverse transition groove planetary roller screw of the present invention.

[0034] Figure 2 yes Figure 1 A partial structural diagram.

[0035] Figure 3 This is a partial structural diagram of the lead screw.

[0036] Figure 4 This is a schematic diagram of the reverse transition slot planetary roller screw in Embodiment 2.

[0037] Figure 5 yes Figure 4 A partial structural diagram.

[0038] Figure 6 yes Figure 5 A partial structural diagram.

[0039] Figure 7 This is a partial structural schematic diagram of the lead screw in Embodiment 2.

[0040] Figure 8 yes Figure 5 A bottom view.

[0041] Figure 9 This is a schematic diagram of the reverse transition slot planetary roller screw in Embodiment 3.

[0042] Figure 10 yes Figure 9 A partial structural diagram.

[0043] Figure 11 yes Figure 10 Side view.

[0044] Figure 12 This is a partial structural schematic diagram of the lead screw in Embodiment 3.

[0045] Figure 13 yes Figure 10 The left view.

[0046] In the diagram: 1. Lead screw; 11. First annular groove; 12. Annular groove group; 13. Insert groove; 2. Nut; 3. Planetary carrier; 31. End plate; 32. Circular hole; 4. Roller; 41. Reference roller; 42. Auxiliary roller; 43. Transmission section; 44. Connecting section; 45. Second annular groove; 5. Limiting component. Detailed Implementation

[0047] The present invention will now be described in further detail with reference to the accompanying drawings. These drawings are simplified schematic diagrams, illustrating only the basic structure of the invention, and therefore only show the components relevant to the invention.

[0048] like Figures 1 to 13 As shown (the nut in the figure is shown in a half-section form, the actual nut is a closed structure), a reverse transition groove planetary roller screw includes a screw 1, n nuts 2 and a transmission assembly disposed between the screw 1 and the nuts 2. The nuts 2 and the screw 1 move relative to each other through the transmission assembly, where n≥1 and n is a positive integer.

[0049] Nut 2 is coaxially sleeved on the outer side of lead screw 1. A transmission assembly is installed inside nut 2. The transmission assembly includes a planetary carrier 3 and multiple rollers 4. The multiple rollers 4 are arranged in a ring around the lead screw 1, and the axial direction of the rollers 4 is parallel to that of the lead screw 1. To ensure stable sliding between nut 2 and lead screw 1, the total number of rollers 4 is at least three. The planetary carrier 3 includes two end plates 31. The two ends of the rollers 4 are defined as connecting sections 44. The end plates 31 are provided with circular holes 32 for mounting the rollers 4. The connecting sections 44 are inserted into the circular holes 32, so that each roller 4 can be... The planetary carrier 3 is fitted around the outer side of the lead screw 1 to rotate about its own axis. Limiting elements 5 are provided at both ends of the planetary carrier 3. These limiting elements 5 can be retaining rings. When the limiting element 5 is a retaining ring, a groove 13 for installing the retaining ring is provided on the outer wall of the lead screw 1. The retaining ring is used to restrict the axial movement of the planetary carrier 3. Furthermore, a stepped surface facing the connecting section 44 is provided between the connecting section 44 and the main body of the roller 4. When the connecting section 44 is inserted into the circular hole 32, the stepped surface abuts against the end of the planetary carrier 3, thereby stabilizing the relative position between the roller 4 and the planetary carrier 3. In other embodiments, the limiting element 5 can be formed as a limiting step on the outer wall of the lead screw 1, with the limiting step located at both ends of the planetary carrier; the limiting element 5 can also be an end plug that is interference-fitted with the lead screw 1 and inserted into both ends of the lead screw 1.

[0050] Specifically, the outer wall of the lead screw 1 is provided with several parallel first annular grooves 11 along its axial direction. The several first annular grooves 11 are divided into multiple annular groove groups 12, and the distance between adjacent annular groove groups 12 is d.

[0051] Each roller 4 is equipped with a transmission section 43, the diameter of which is larger than the rest of the roller 4. The transmission section 43 has parallel second annular grooves 45. The rest of the roller 4 is a smooth shaft. Each transmission section 43 on each roller 4 is positioned opposite a set of annular grooves 12. The groove spacing between the first annular grooves 11, the groove spacing between the second annular grooves 45, and the pitch (M) of the nut 2 are all equal in each set of annular grooves 12. Therefore, the roller 4 meshes with the nut 2 and the lead screw 1 through the transmission section 43. It should be noted that the number of first annular grooves 11 in each set of annular grooves 12 is greater than or equal to one, the number of second annular grooves 45 on each transmission section 43 is less than or equal to the number of first annular grooves 11 in the corresponding set of annular grooves 12, and the number of second annular grooves 45 on each transmission section 43 is greater than or equal to one.

[0052] Furthermore, in order to enable the transmission assembly to smoothly drive the lead screw 1 and nut 2 to slide relative to each other, the following design is made for the spacing d between adjacent annular groove groups 12:

[0053] The multiple rollers 4 include multiple auxiliary rollers 42 and n reference rollers 41. The number of reference rollers 41 is equal to the number of heads of nut 2. The number of auxiliary rollers 42 can be 0, that is, nut 2 with three or more heads can only have reference rollers 41. The n reference rollers 41 mesh with the same annular groove group 12 on the lead screw 1. The n reference rollers 41 are evenly distributed around the lead screw 1. The included angle between adjacent reference rollers 41 is β=360° / n.

[0054] The area between adjacent reference rollers 41 is the design interval. The annular groove group 12 opposite to the transmission section 43 on the reference roller 41 is the reference groove group. Within each design interval, taking the reference groove group as the 0th annular groove group 12, the distance between the i-th annular groove group 12 and the (i-1)-th annular groove group 12 along the axial direction of the lead screw 1 is... Where M is the pitch of nut 2. Let k be the angle between the roller 4 corresponding to the k-th annular groove group 12 and a reference roller 41 at the end of its design section, where k = i or i-1, i is a positive integer, and the reference roller 41 is considered to be the 0th roller. It is 0 degrees.

[0055] When the number of rollers 4 is greater than or equal to three, in order to simplify the design, the number of reference rollers 41 or auxiliary rollers 42 can be appropriately reduced. That is, among the multiple rollers 4, at least three rollers 4 are solid, and the rest are virtual rollers 4.

[0056] When the lead screw 1 is axially fixed and rotates, the nut 2 moves along the axial direction of the lead screw 1. The planetary carrier 3 and multiple rollers 4 revolve within the nut 2, and the planetary carrier 3 moves with the lead screw 1. Simultaneously, each roller 4 rotates around its own axis.

[0057] The present invention generates axial rigid constraint on the roller 4 through the mutual meshing between the second annular groove 45 on the transmission section 43 and the first annular groove 11 in the annular groove group 12; through the leap-type design of the spacing d between the annular groove groups 12, the correct meshing between the roller 4 and the nut 2 and the lead screw 1 is realized, the planetary motion of the roller 4 revolving and rotating between the lead screw 1 and the nut 2 is realized, and the relative sliding between the lead screw 1 and the nut 2 is realized.

[0058] Compared to traditional forward-rotating planetary roller screw structures, the annular groove structure eliminates the complex combination of gears and threads. Its simplicity significantly reduces the machining difficulty of planetary roller screws, and its precision is easily controlled, making it suitable for large-scale, low-cost, and high-precision production. Simultaneously, the simple design of the retaining rings at both ends of the planetary carrier 3 abutting against the stepped surfaces of the rollers 4 effectively constrains the axial and radial displacement of the rollers 4, ensuring smooth transmission and the effectiveness of the entire transmission mechanism. This solution enables even a conventional single-headed nut 2 to achieve a stable arrangement of at least three rollers and provides precise feed capability, offering a simplified and cost-effective high-performance solution for applications requiring non-self-locking, constant lead small-lead movement.

[0059] It should be noted that the cross-sectional shape of the first annular groove 11, the cross-sectional shape of the second annular groove 45, and the cross-sectional shape of the thread on the lead screw are not limited, and can be, but are not limited to, the following shapes: triangular, trapezoidal, circular arc, and involute tooth profile.

[0060] It should be noted that the tooth surface of the tooth formed by the second annular groove 45 on the transmission section 43 is a convex arc surface.

[0061] Example 1:

[0062] like Figures 1 to 3 As shown, in this embodiment, the nut 2 is a single-headed nut, the number of reference rollers 41 is one, the design interval in this embodiment is one, and there are two auxiliary rollers 42 in this embodiment. The three rollers 4 are evenly distributed around the screw 1, and the included angle between adjacent rollers 4 is 120°.

[0063] Within the design range, starting from the reference roller 41, looking clockwise:

[0064] The angle between the first auxiliary roller 42 and the reference roller 41 The angle between the second auxiliary roller 42 and the reference roller 41 is 120°. It is 240°;

[0065] The distance between the annular groove group 12 corresponding to the first auxiliary roller 42 and the reference groove group ;

[0066] The distance between the annular groove group 12 corresponding to the second auxiliary roller 42 and the previous annular groove group 12 In this embodiment, the lead screw 1 is provided with three annular groove groups 12.

[0067] Example 2:

[0068] like Figures 4 to 8As shown, in this embodiment, the nut 2 is a double-ended nut, and there are two reference rollers 41. The two reference rollers 41 are arranged opposite each other with an included angle of 180°. The two reference rollers 41 mesh with the same annular groove group 12. In this embodiment, there are two designed intervals. In this embodiment, there are two auxiliary rollers 42. The four rollers 4 are evenly distributed around the screw 1, and the included angle between adjacent rollers 4 is 90°.

[0069] Within each design interval, starting from the reference roller 41, look clockwise:

[0070] The angle between the auxiliary roller 42 and the reference roller 41 in the first design interval The angle is 90°, which is the distance between the annular groove group 12 corresponding to the auxiliary roller 42 and the reference groove group. ;

[0071] The angle between the auxiliary roller 42 and the corresponding reference roller 41 in the second design interval The angle is 90°, which is the distance between the annular groove group 12 corresponding to the auxiliary roller 42 and the reference groove group. ;

[0072] The spacing between the two auxiliary rollers 42 and the reference groove group 12 is equal. The two auxiliary rollers 42 mesh with the same annular groove group 12. In this embodiment, the lead screw 1 is provided with two annular groove groups 12.

[0073] Example 3:

[0074] like Figures 9 to 13 As shown, in this embodiment, the nut 2 is a three-headed nut, and there are three reference rollers 41. The three rollers are equidistantly arranged circumferentially with an included angle of 120° between them. The three base rollers 4 mesh with the same annular groove group 12. In this embodiment, there are three design intervals. In this embodiment, there are three auxiliary rollers 42. The six rollers 4 are evenly distributed around the screw 1, and the included angle between adjacent rollers 4 is 60°.

[0075] In this embodiment, the optimal number of rollers 4 is 6 (different from the number of rollers in Embodiment 1), and the number of annular groove groups of the lead screw 1 is 2 (same as Embodiment 2).

[0076] Within each design interval, starting from the reference roller 41, look clockwise:

[0077] The angle between the auxiliary roller 42 and the reference roller 41 in the first design interval The angle is 60°, which is the distance between the annular groove group 12 corresponding to the auxiliary roller 42 and the reference groove group. ;

[0078] The angle between the auxiliary roller 42 and the corresponding reference roller 41 in the second design interval The angle is 60°, which is the distance between the annular groove group 12 corresponding to the auxiliary roller 42 and the reference groove group. ;

[0079] The angle between the auxiliary roller 42 and the corresponding reference roller 41 in the third design interval The angle is 30°, which is the distance between the annular groove group 12 corresponding to the auxiliary roller 42 and the reference groove group. ;

[0080] The spacing between the three auxiliary rollers 42 and the reference groove group 12 is equal. The three auxiliary rollers 42 mesh with the same annular groove group 12. In this embodiment, the lead screw 1 is provided with two annular groove groups 12.

[0081] Preferably, in this embodiment, since the number of reference rollers 41 meets the minimum number of rollers in the structural design, auxiliary rollers 42 can be omitted in this embodiment. From the perspective of load capacity, the more rollers 4 there are, the greater the load. Therefore, when the nut 2 is a three-headed nut, it is preferable to evenly distribute six rollers 4.

[0082] Based on the above-described preferred embodiments of the present invention, and through the foregoing description, those skilled in the art can make various changes and modifications without departing from the inventive concept. The technical scope of this invention is not limited to the contents of the specification, but must be determined according to the scope of the claims.

Claims

1. A reverse-type transition slot planetary roller screw, characterized in that: include: The lead screw (1) has a plurality of parallel first annular grooves (11) on its outer side wall along its axial direction. The plurality of first annular grooves (11) are divided into a plurality of annular groove groups (12), and the distance between adjacent annular groove groups (12) is d. Nut (2), the nut (2) is coaxially sleeved on the outside of the lead screw (1); Multiple rollers (4) are arranged in a ring between the lead screw (1) and the nut (2). The multiple rollers (4) are mounted on the outer wall of the lead screw (1) through the planetary carrier (3). The axial direction of the rollers (4) is parallel to that of the lead screw (1). Each roller (4) is provided with a transmission section (43). The transmission section (43) has parallel second annular grooves (45). The transmission section (43) on each roller (4) is arranged opposite to an annular groove group (12). The pitch of the nut (2), the groove distance between adjacent first annular grooves (11) in the same annular groove group (12), and the groove distance between adjacent second annular grooves (45) are all equal. The rollers (4) mesh with the nut (2) and the lead screw (1) through the transmission section (43). The total number of rollers (4) is at least three; The number of heads of the nut (2) is n, n≥1, and the multiple rollers (4) include n reference rollers (41) and multiple auxiliary rollers (42). The n reference rollers (41) mesh with the same annular groove group (12). n reference rollers (41) are evenly distributed around the screw (1) in the circumference, and the included angle between adjacent reference rollers (41) is β=360° / n; The area between adjacent reference rollers (41) is the design interval. The annular groove group (12) opposite to the transmission section (43) on the reference roller (41) is the reference groove group. Taking the reference groove group as the 0th annular groove group (12), the distance between the i-th annular groove group (12) and the (i-1)-th annular groove group (12) along the axial direction of the lead screw (1) is... Where M is the pitch of the nut. The angle between the auxiliary roller (42) corresponding to the kth annular groove group (12) and a reference roller (41) at the end of its design section, k=i or i-1; It is 0 degrees.

2. The reverse-type jump-slot planetary roller screw according to claim 1, characterized in that: Multiple rollers (4) are evenly distributed around the screw (1) in the circumferential direction.

3. The reverse-type jump-slot planetary roller screw according to claim 1, characterized in that: The lead screw (1) is provided with a limiting member (5), which is used to limit the axial sliding of the planet carrier (3).

4. The reverse-type jump-slot planetary roller screw according to claim 3, characterized in that: The limiting member (5) is provided with two respectively located at both ends of the planetary carrier (3), and the lead screw (1) is provided with a groove (13) for embedding the limiting member (5).

5. The reverse-type jump-slot planetary roller screw according to claim 1, characterized in that: The planetary carrier (3) has a circular hole (32) at its end for inserting the end of the roller (4).

6. The reverse-type jump-slot planetary roller screw according to claim 5, characterized in that: The end of the roller (4) is provided as a connecting section (44). A stepped surface is provided between the connecting section (44) and the main body of the roller (4) facing the connecting section (44). When the connecting section (44) is inserted into the round hole (32), the stepped surface abuts against the end of the planet carrier (3).

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