WO2012146579A1 - Transmission destinée à convertir des mouvements rotatifs, roue de transmission pour une telle transmission et utilisation d'une telle transmission - Google Patents

Transmission destinée à convertir des mouvements rotatifs, roue de transmission pour une telle transmission et utilisation d'une telle transmission Download PDF

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Publication number
WO2012146579A1
WO2012146579A1 PCT/EP2012/057465 EP2012057465W WO2012146579A1 WO 2012146579 A1 WO2012146579 A1 WO 2012146579A1 EP 2012057465 W EP2012057465 W EP 2012057465W WO 2012146579 A1 WO2012146579 A1 WO 2012146579A1
Authority
WO
WIPO (PCT)
Prior art keywords
transmission
gear
shaft
shafts
rotatably mounted
Prior art date
Application number
PCT/EP2012/057465
Other languages
German (de)
English (en)
Inventor
Walter Mathis
Original Assignee
Sinell Ag
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Sinell Ag filed Critical Sinell Ag
Publication of WO2012146579A1 publication Critical patent/WO2012146579A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/02—Toothed gearings for conveying rotary motion without gears having orbital motion
    • F16H1/04—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members
    • F16H1/12—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with non-parallel axes
    • F16H1/16—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with non-parallel axes comprising worm and worm-wheel
    • F16H1/166—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with non-parallel axes comprising worm and worm-wheel with members rotating around axes on the worm or worm-wheel

Definitions

  • the present invention relates to a transmission for
  • Speed of the drive shaft converted into a higher or lower speed of the output shaft is usually accompanied by a corresponding implementation of a force or torque.
  • DE 3307405 AI describes such a worm gear with a worm and a worm wheel, at the edge of a plurality of rotatably mounted, designated as rolling elements wheels are arranged. These wheels engage in one
  • the wheels act friction reducing and that due to the large contact surface of the wheels, a correspondingly low surface pressure occurs, so that by means of the wheels large forces can be implemented.
  • the construction is relatively complex.
  • the object of the present invention is to provide an improved transmission for the uniform transfer of
  • helical groove and a gear including a plurality of individually rotatably mounted about a rotational axis shafts.
  • the rotatably mounted shafts are arranged such that at least one of the rotatably mounted shafts engages in the helical groove of the transmission shaft to implement rotational movements between the transmission shaft and the gear.
  • the rotatably mounted shafts are mounted on one side in the gear, so that their free ends serve the intervention in the helical groove extending.
  • the rotatably mounted shafts act as form-fitting elements, so that these both for the implementation of
  • Rotational movements and forces are suitable. In this sense, in the following under an implementation of rotational movements always a possible implementation of forces with or without corresponding rotational movement to understand, for example, a use of the transmission as a barrier.
  • the implementation of the rotational movement can take place in the direction from the transmission shaft to the gear. It is the
  • the waves are arranged at regular intervals along the edge of the gear, so that there is a symmetrical distribution of the gear.
  • a symmetrical division is given directly by the number of regularly arranged waves.
  • the division characterizes the design of the transmission and thus the implementation of the rotational movements, in particular their under or transmission ratio.
  • This division is typically matched to the design of the transmission shaft, in particular on the helical groove extending. In a similar way, the
  • Gear wheels are tuned or the transmission shaft and the gear are tuned together.
  • the one-sided mounting of the shaft means that the shaft is basically subdivided into a first section and a second section adjoining it axially with respect to the axis of rotation, wherein the first section serves to rotatably support the shaft and the second section forms a free end which adjoins another Components, in this case to the groove of the transmission shaft, can be coupled.
  • the first section regarding the
  • Rotary axis divided into two parts, wherein the first part is adjacent to the free end of the shaft and the radial bearing of the shaft is used and the second part is arranged opposite the free end of the shaft and the axial support of the shaft.
  • first portion or its first part by means of spherical caps, in particular two
  • Edge pressures at the shaft and / or at the gear wheel are reduced or eliminated.
  • the unilaterally mounted shafts have the advantage over the known from the prior art wheels that no wheel-shaped configuration on the shaft for engaging in the groove of the transmission shaft is needed. Therefore, these waves can be built very compact and robust.
  • the diameter of the first portion of the shaft may be equal to or even greater than the diameter of the free end.
  • helical is to be understood as a substantially helically wound structure on which the surface of a rotationally symmetrical body is based, for example a rotational hyperboloid, a globoid or, as a special case, a cylinder. It is under a helical groove and a
  • the rotatably mounted shafts are arranged such that upon engagement, the free ends of the shafts extend at least partially on a flank of the helical Unroll the groove. This rolling allows a conversion of the rotational movements by means of low-friction rolling processes.
  • the rotatably mounted shafts are arranged such that when engaging the free end of a first of the waves at least partially rolls on a first edge of the groove and the free end of a second of the waves at least partially on one, the first edge unrolled opposite second edge of the groove.
  • the rotatably mounted shafts are arranged such that the axes of rotation of the shafts are aligned at the apex of the engagement substantially perpendicular to the axis of rotation of the transmission shaft. This avoids incorrect angles and resulting friction losses.
  • the groove of the gear shaft is designed such that it is tuned to the geometric rolling characteristics of the waves in the groove.
  • the angle between the axis of rotation of the shaft and the axis of rotation changes the transmission shaft continuously.
  • the axial pitch and / or the pitch may change depending on the distance from the vertex. For example, the pitch of the helical groove decreases in a globoid from
  • the tuning relating to this rolling characteristic can be achieved on the one hand by choosing a suitable radial pitch of the gear, e.g. be achieved by a corresponding geometric arrangement of the waves, and / or by selecting a suitable axial pitch of the transmission shaft. With this vote, a substantial compensation of the changing angles is achieved, so that from these angle changes
  • the rotatably mounted shafts are arranged such that the axes of rotation of the shafts are aligned at the apex of the engagement substantially perpendicular to the surface of the gear.
  • the rotatably mounted shafts are arranged so that they are separated from each other in the axial direction of the
  • Gear arranged spaced apart form groups Gear arranged spaced apart form groups.
  • Waves in a group and on the other hand from the Space of the spaced groups Due to the larger available space optimal adaptation of the storage of the individual waves, in particular their arrangement and / or structure, to the required design and / or the intended performance of the transmission is achieved (eg low friction, high gear ratio, large
  • the rotatably mounted shafts are arranged so that they form two separate, spaced from each other in the axial direction of the gear arranged groups.
  • Other forms of groups may also be formed, for example a three group arrangement, i. a middle group with two fringe groups.
  • the waves of the spaced-apart groups are angularly offset, so that the axes of rotation of the waves have different angles of rotation with respect to the axis of rotation of the gear and a radially directed thereto, common origin direction.
  • an optimal adaptation of the waves to the geometric conditions of the groove of the gear shaft and in particular to the design of the flanks is achieved.
  • standing waves are balanced symmetrically in the middle.
  • the rotatably mounted shafts are arranged such that the distance between two adjacent waves corresponds to a multiple, in particular twice, the pitch of the helically extending groove.
  • the pitch is to be understood as the distance to which the
  • neighboring wave is a neighbor from the same group.
  • This arrangement of the individual waves is more space for the arrangement and design of storage available. Thus, a very stable storage of the waves can be realized. In addition, there are cost savings.
  • the rotatably mounted shafts are axially displaceable stored and / or biased.
  • a plurality of rotatably mounted shafts are braced against each other by each engaging with such a bias on the opposite edges of the helical groove.
  • such a preload acts to dampen an overload or a shock load of the transmission shaft, the gear or the entire transmission.
  • the gear is in one piece and / or the rotatably mounted shafts are mounted on one side.
  • the rotatably mounted shafts are locked in the gear by a, in particular screwable, lock.
  • the free ends are dome-shaped, in particular conical.
  • the transmission shaft is a Globiod.
  • Circulation speed and the changing clearance angle are compensated.
  • complicated mechanisms are used in the prior art, for example, shafts with rotatably mounted axes of rotation and / or
  • the waves automatically compensate for the aforementioned changes by simple speed changes.
  • the length of the gear shaft or its helically extending groove is formed such that the number of rotatably mounted shafts respectively engaged is substantially constant. The beginning of the engagement of a shaft in the groove on a first side of the transmission shaft thus leads to the first side opposite side of the transmission shaft to a substantially simultaneous emergence of another wave, which has previously intervened in the groove. This will be a uniform
  • the transmission has an additional shaft, which with
  • Transmission shaft is arranged opposite side of the gear. This will split the
  • the play-free transmission by a be achieved by means of gear shaft and additional shaft generated bias.
  • the auxiliary shaft is angled to the transmission shaft
  • the present invention relates to a
  • Gear for a transmission according to one of the preceding embodiments.
  • the present invention relates to a
  • this is, at least partially, designed for multi-way, in particular symmetrical split, power transmission. This allows forces within the transmission system, in particular bearing forces of the gears and / or
  • the diameter of the gear of the additional gear is smaller than the diameter of the
  • Gear wheel one of the above-mentioned transmission design in particular, the smaller diameter is at least 80%, more preferably at least 50%, of the larger diameter.
  • Material savings can be achieved and / or the number of required rotatably mounted shafts can be reduced.
  • this dimensioning of the gears is combined with the above-mentioned angular arrangement of the transmission shaft or the additional shaft, so that a very compact construction of the transmission system is achieved.
  • the additional gear on an additional gear shaft with a helical groove, wherein the additional gear shaft directly to the transmission shaft of the
  • erfindungsmässen transmission is coupled, in particular together with this forms a common shaft, and wherein at least one of the rotatably mounted shafts of the
  • Gear of the additional gear engages in the helical groove extending the additional gear shaft.
  • the transmission system can be constructed as a so-called angular gear, ie the output direction of the
  • Transmission system is angled to the input direction of the
  • the input direction corresponds to the axis of rotation of the force-receiving gear shaft or of the force-absorbing gear and the output direction of the axis of rotation of the force-emitting gear shaft or of the force-transmitting gear.
  • Exit direction substantially perpendicular, i. about 90 °, to the input direction.
  • Such an angle gear allows a flexible
  • the present invention relates to
  • Embodiments or a transmission system according to one of the preceding embodiments as a transmission gear, in particular in a wind generator. Thereby, a high number of revolutions of the transmission shaft can be efficiently generated. Therefore, this use is suitable
  • Embodiments or combinations of combinations may be the subject of a further combination. Only those combinations are excluded that would lead to a contradiction.
  • Fig. 1 is a schematically simplified and perspective
  • FIG. 2 shows a cross section through the transmission according to FIG.
  • FIG. 3 shows a detail view for fastening the rotatably mounted shaft 22 according to FIG. 2;
  • Fig. 4 is a detail view of another embodiment of the
  • FIG. 5 shows an illustration of the transmission according to FIG. 1 with an additional shaft 30;
  • Fig. 6 is a schematically simplified and perspective
  • FIG. 7 is an illustration of a transmission system according to FIG.
  • Fig. 1 shows a schematically simplified
  • Gear 20 has.
  • Rotary movement of the transmission shaft 10 causes the gear 20.
  • the transmission can also be done in the
  • the gear shaft 10 is formed as Globiod, on whose lateral surface a helical groove 12 extends.
  • the groove 12 has a first flank 14 and a first flank 14 opposite the second flank 18.
  • the gear 20 is mentally divided into a wheel-shaped first part 21a and a wheel-shaped second part 21b, which in the axial direction of the
  • Gear 20 connects to the first part 21a.
  • the first part 21a is conically tapered in the direction of the second part 21b and thereby forms a first bevel of the gear wheel 20.
  • the second part 21b tapers conically towards the first part 21a and thereby forms a second bevel of the gear wheel 20.
  • representative of the group of waves of the first part 21a is a first shaft 22 and a second shaft 26 representative of the group of waves of the second part 21b.
  • the first shaft 22 and the second shaft 26 are arranged so as to represent two separately arranged groups which are spaced from each other in the axial direction of the gear 20.
  • All shafts are individually mounted for rotation about a rotation axis D (shown only for the shaft 22).
  • the first shaft 22, or its associated group of shafts is mounted on one side in the gear wheel 20, so that the first shaft 22 has a free end 24.
  • Rotary axes of the shafts 22 and 26 have different angles of rotation with respect to the axis of rotation of the gear and a radially directed thereto, common origin direction. That is, the shafts 22 and 26 are at different angles of rotation with respect to the cylindrical coordinates of the
  • the offset allows the engagement of the free ends 24 and 28 in the helical groove 12 of the transmission shaft 10.
  • the free ends 24 and 28 are tapered so that they are adapted for the
  • the diameter of the free end 24 must always be smaller than the width of the groove 12 to a simultaneous
  • Fig. 2 shows a cross section through the transmission according to FIG. 1.
  • the arranged in the gear 20 shaft 22 engages in the transmission shaft 10 a.
  • the free end 24 of the rotatably mounted shaft 22 rolls on the first flank 14 of the transmission shaft 10.
  • the shaft 22 is mounted axially displaceable and biased by a spring device. This will be a
  • Fig. 3 shows a detailed view of the attachment of the shaft 22 as shown in FIG. 2. In order to achieve an axially displaceable mounting of the shaft 22, this is by means of two
  • Gear 20 are transmitted.
  • the spherical caps 21a can automatically align themselves in accordance with the respectively acting forces, so that edge pressures in the shaft 22 and / or in the gear wheel 20 are avoided.
  • the bearing can also be designed as plain bearings, in particular taking into account suitable
  • the shaft 22 is biased by a spring device.
  • the spring device on the free end 24 opposite side of the shaft 22nd is biased by a spring device.
  • the spring device essentially comprises a ball bearing 25a, a washer 25b, a plunger 25c and a spring 25d.
  • the plunger 25c is axially displaceable, but not rotatably mounted and is pressed by the spring 25d in the direction of the shaft 22. Between the plunger 25c and the shaft 22, however, the intermediate disc 25b and the ball bearing 25a are still arranged.
  • the intermediate disc 25b serves to uniformly distribute the force effect of the plunger 25c on the ball bearing 25a.
  • the ball bearing 25a on the other hand, on the one hand causes the forwarding of the
  • the gear wheel 20 comprises a shoulder 21b, on which the intermediate disc 25b rests during the resting phase.
  • the rest phase of the shaft 22 denotes that time during the rotation of the gear, in which no engagement of the respective shaft 22 in the groove of the
  • Transmission shaft (see reference numeral 12 of Fig. 1) takes place and the shaft 22 is therefore radially and axially unloaded.
  • the spring force which acts on the intermediate disc 25b via the plunger 25c, is guided via the shoulder 21b and received by the gear 20.
  • the unloaded shaft 22 by means of a free end 24th
  • Transmission shaft (see reference numeral 12 of Fig. 1), the shaft 22 is first lifted from the support surface 21d, so that the shaft 22 until after this lifting on the
  • Friction losses which are in connection with the resting of the shaft 22 on the support surface 21d, are largely reduced or eliminated.
  • FIG. 4 shows a detailed view of a further embodiment for mounting the rotatably mounted shaft 22 according to FIG. 3 with a device for supporting the shaft 22 and a lock 28.
  • the device for fixing the shaft 22 is formed in the form of a bearing cartridge 27 and in this example comprises the two spherical caps, the roller bearing, the spring device for generating the bias of the shaft 22 and the shoulder, which serves as a support during the rest phase of the shaft 22.
  • the bearing cartridge 27 and thus the shaft 22 is mounted on one side, that is, the gear 20 and the
  • Bearing cartridge 27 are formed such that the
  • Gear 20 can be mounted.
  • the gear 20 is in one piece, that is, the gear 20 is in
  • Gear 20 are then used below the waves 22 - an assembly of the gear deleted.
  • the bearing cartridge 27 including the shaft 22 forms a compact unit. This unit can be prepared in advance and in a later
  • the bearing cartridge 27 is held by means of a conical seat and the lock 28 in the intended position in the gear.
  • the lock 28 by means of a screw 29 on
  • the storage cartridge 27 can also by means of a cylindrical seat or by means of a
  • Thread be attached in the gear.
  • the end position of the bearing cartridge 27 in the gear 20 is adjustable.
  • the end position of the bearing cartridge 27 by a lock, in particular by the above-described screw-lock 28, are fixed.
  • FIG. 5 shows a representation of the transmission according to FIG. 1 with an additional shaft 30.
  • the additional shaft 30 is on the side of the transmission shaft 10 opposite
  • Gear 20 arranged and has a helical groove extending.
  • the additional shaft 30 cooperates with the rotatably mounted shafts of the gear 20, so that at least one of the rotatably mounted shafts engages in the helical groove extending the auxiliary shaft 30 to rotational movements between the additional shaft 30 and the
  • Gear 20 implement.
  • the axis of the auxiliary shaft 30 is aligned parallel to the axis of the transmission shaft 10.
  • the auxiliary shaft 30 is constructed identically to the transmission shaft 10, so that the helical groove extending the auxiliary shaft 30th
  • Fig. 6 shows a schematically simplified
  • FIG. 5 perspective view of a transmission system with a transmission according to FIG. 5 and with an additional transmission.
  • the additional gear includes two gears 40 and 50 and a further auxiliary shaft 60.
  • the additional gear is connected to the transmission according to FIG. 5 in series, so that a rotational movement of the transmission according to FIG. 5 on the
  • the gear wheels 40 and 50 are identical to the gear wheel according to FIG. 5 and the additional additional shaft 60 identical to the auxiliary shaft 10 and 30 according to FIG. 5.
  • the gear wheels 40 and 50 are identical to the gear wheel according to FIG. 5 and the additional additional shaft 60 identical to the auxiliary shaft 10 and 30 according to FIG. 5.
  • Such a power transmission can also with combinations of different transmission shafts and / or
  • a symmetrical split power transmission is particularly advantageous for applications where large forces are to be implemented, especially in the translation of lower to higher speeds, for example in one
  • FIG. 7 shows an illustration of a transmission system according to FIG. 6, but with the additional shaft 30 arranged at an angle to the transmission shaft 10. It was at the
  • Axial distance to project orthogonal plane and the axis angle is to be determined on the basis of these projections.
  • the diameters of the two gear wheels 40 and 50 are less than 50% of the diameter of the gear 20.
  • the diameter of the additional auxiliary shaft 60 is smaller than the diameter of the transmission shaft 10 and the additional shaft 30th
  • this structure is very advantageous in a large-scale transmission system, which in particular has a weight of at least 1 ton, more particularly at least 10 tons, for example in a transmission system for a

Abstract

L'invention concerne une transmission destinée à la conversion uniforme de mouvements rotatifs, ladite transmission comprenant un arbre de transmission (10) doté d'au moins une rainure (12) s'étendant de façon hélicoïdale et une roue de transmission (20) dotée de plusieurs arbres (22) montés rotatifs de manière à pouvoir tourner respectivement individuellement autour d'un axe de rotation (D). Les arbres (22, 26) montés rotatifs sont disposés de telle sorte qu'au moins un des arbres (22, 26) se loge dans la rainure (12) s'étendant de façon hélicoïdale de l'arbre de transmission (10), afin de transférer des mouvements rotatifs entre l'arbre de transmission (10) et la roue de transmission (20). Les arbres (22, 26) sont montés d'un côté dans la roue de transmission (20), de sorte que leurs extrémités libres (24, 28) servent au logement dans la rainure (12) s'étendant de façon hélicoïdale.
PCT/EP2012/057465 2011-04-26 2012-04-24 Transmission destinée à convertir des mouvements rotatifs, roue de transmission pour une telle transmission et utilisation d'une telle transmission WO2012146579A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH7112011A CH704874A2 (de) 2011-04-26 2011-04-26 Getriebe zum Umsetzen von Drehbewegungen, Getrieberad für ein solches Getriebe und Verwendung eines solchen Getriebes.
CH00711/11 2011-04-26

Publications (1)

Publication Number Publication Date
WO2012146579A1 true WO2012146579A1 (fr) 2012-11-01

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PCT/EP2012/057465 WO2012146579A1 (fr) 2011-04-26 2012-04-24 Transmission destinée à convertir des mouvements rotatifs, roue de transmission pour une telle transmission et utilisation d'une telle transmission

Country Status (2)

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CH (1) CH704874A2 (fr)
WO (1) WO2012146579A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20220018428A1 (en) * 2020-07-15 2022-01-20 Chui-Tsai CHIU Double row roller cam transmission mechanism with backlash adjustment means
CN113958673A (zh) * 2020-07-20 2022-01-21 邱垂财 无背隙双列式滚子凸轮传动装置

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013113722A1 (de) * 2013-12-09 2015-06-11 Weiss Gmbh Antriebseinheit
DE102016010092B3 (de) * 2016-08-24 2017-11-16 Olaf und André Tünkers GbR (vertretungsber. Gesellsch. Dipl.-Ing. Olaf Tünkers, 40880 Ratingen und Dipl.-Wirt.-Ing. André Tünkers, 40880 Ratingen) Drehtisch

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1273533A (en) * 1917-12-03 1918-07-23 William Q Pfahler Worm-drive.
DE333649C (de) * 1919-10-05 1921-03-03 Henry Seemann Schnecke fuer Schneckengetriebe
DE1041315B (de) * 1955-03-05 1958-10-16 Walter Obereichholz Schnecken- bzw. Schraubspindeltrieb
DE977207C (de) * 1952-12-24 1965-06-10 Schiess Ag Zahnrad-Waelzfraesmaschine
US3495470A (en) * 1968-04-03 1970-02-17 Joseph P Mccartin Spherical thread and pin gear reduction
DE3307405A1 (de) 1982-03-03 1983-09-08 Isao Narashino Chiba Nemoto Leistungsuebertragungsvorrichtung
US4685346A (en) * 1984-03-13 1987-08-11 Maxaxam Corporation Power transmission system
US5960668A (en) * 1996-10-25 1999-10-05 National Science Council Indexing mechanism using pairs of radially disposed rollers engaged between adjacent cam ribs
US20080279686A1 (en) * 2006-01-25 2008-11-13 Jens Demtroder Wind Turbine Comprising At Least One Gearbox And An Epicyclic Gearbox

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1273533A (en) * 1917-12-03 1918-07-23 William Q Pfahler Worm-drive.
DE333649C (de) * 1919-10-05 1921-03-03 Henry Seemann Schnecke fuer Schneckengetriebe
DE977207C (de) * 1952-12-24 1965-06-10 Schiess Ag Zahnrad-Waelzfraesmaschine
DE1041315B (de) * 1955-03-05 1958-10-16 Walter Obereichholz Schnecken- bzw. Schraubspindeltrieb
US3495470A (en) * 1968-04-03 1970-02-17 Joseph P Mccartin Spherical thread and pin gear reduction
DE3307405A1 (de) 1982-03-03 1983-09-08 Isao Narashino Chiba Nemoto Leistungsuebertragungsvorrichtung
US4685346A (en) * 1984-03-13 1987-08-11 Maxaxam Corporation Power transmission system
US5960668A (en) * 1996-10-25 1999-10-05 National Science Council Indexing mechanism using pairs of radially disposed rollers engaged between adjacent cam ribs
US20080279686A1 (en) * 2006-01-25 2008-11-13 Jens Demtroder Wind Turbine Comprising At Least One Gearbox And An Epicyclic Gearbox

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20220018428A1 (en) * 2020-07-15 2022-01-20 Chui-Tsai CHIU Double row roller cam transmission mechanism with backlash adjustment means
CN113958673A (zh) * 2020-07-20 2022-01-21 邱垂财 无背隙双列式滚子凸轮传动装置

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