JP2011064623A - Surveying instrument - Google Patents

Surveying instrument Download PDF

Info

Publication number
JP2011064623A
JP2011064623A JP2009216692A JP2009216692A JP2011064623A JP 2011064623 A JP2011064623 A JP 2011064623A JP 2009216692 A JP2009216692 A JP 2009216692A JP 2009216692 A JP2009216692 A JP 2009216692A JP 2011064623 A JP2011064623 A JP 2011064623A
Authority
JP
Japan
Prior art keywords
bearing
gear
surveying instrument
pressing
pressing member
Prior art date
Legal status (The legal status 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 status listed.)
Granted
Application number
JP2009216692A
Other languages
Japanese (ja)
Other versions
JP5461127B2 (en
Inventor
Makoto Takahashi
誠 高橋
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Nikon Trimble Co Ltd
Original Assignee
Nikon Trimble Co Ltd
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 Nikon Trimble Co Ltd filed Critical Nikon Trimble Co Ltd
Priority to JP2009216692A priority Critical patent/JP5461127B2/en
Publication of JP2011064623A publication Critical patent/JP2011064623A/en
Application granted granted Critical
Publication of JP5461127B2 publication Critical patent/JP5461127B2/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Landscapes

  • Gear Transmission (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To suppress displacement of a gear spindle and reduce an error of differential rotation drive. <P>SOLUTION: A worm gear shaft 15 is rotatably pivoted by a spherical bearing 19 and ball bearings 17 and 18 and can be rocked slightly around the spherical bearing 19. The worm gear shaft 15 is pushed against the worm wheel 30 side by a biasing force of a coil spring 22. The ball bearing 17 is pressed in one direction perpendicular to the direction of pushing, while the ball bearing 18 is pressed in the direction reverse to that one direction. A worm wheel 30 is fitted loose on a horizontal rotation shaft 31. When a first differential operation knob 11 is rotated by hand operation, the torque thereof is transmitted to the worm gear shaft 15 and the worm wheel 30, and a collimating telescope part 4 rotates differentially around the horizontal axis with the rotation of the horizontal rotation shaft 31. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

本発明は、トランシットやセオドライトやトータルステーションやレベルなどの測量機に関し、特に望遠鏡部の視準軸の向きを変える微動回動機構を有する測量機に関する。   The present invention relates to a surveying instrument such as a transit, theodolite, total station, or level, and more particularly to a surveying instrument having a fine movement rotating mechanism that changes the direction of a collimation axis of a telescope unit.

従来の測量機は、視準望遠鏡部を水平軸又は鉛直軸の回りに回転駆動する微動回動機構が設けられている。この微動回動機構は、微動操作ノブと、この微動操作ノブによって回転されるウォームギヤ軸と、このウォームギヤ軸に取り付けられたウォームギヤに噛み合うウォームホイールと、このウォームホイールによって回動され、視準望遠鏡部を回転駆動する回転軸体とを備える。ウォームギヤ軸は、一端部で回転可能かつ揺動可能に軸支され、他端部においてバネによって、ウォームギヤをウォームホイールに押し付ける方向に、付勢される（例えば、特許文献１参照）。   A conventional surveying instrument is provided with a fine rotation mechanism that rotates the collimating telescope unit around a horizontal axis or a vertical axis. The fine movement rotating mechanism includes a fine operation knob, a worm gear shaft rotated by the fine operation knob, a worm wheel meshing with a worm gear attached to the worm gear shaft, and a collimating telescope unit rotated by the worm wheel. And a rotating shaft body for rotationally driving. The worm gear shaft is pivotally supported at one end so as to be rotatable and swingable. At the other end, the worm gear shaft is biased by a spring in a direction in which the worm gear is pressed against the worm wheel (see, for example, Patent Document 1).

特許公報第２６８１２２１号Japanese Patent No. 2681221

ところが、上述した従来の測量機は、ウォームギヤをウォームホイールに押し付けるために、ウォームギヤ軸をその一端部で揺動可能に軸支しているので、微動回転操作中にウォームギヤ軸が上述の押し付け方向に垂直な方向に変位してしまい、この変位によって微動回転駆動に誤差が生じるという問題がある。   However, in the conventional surveying instrument described above, the worm gear shaft is pivotally supported at one end thereof in order to press the worm gear against the worm wheel. There is a problem that displacement occurs in the vertical direction, and this displacement causes an error in the fine motion rotation drive.

（１）請求項１の発明による測量機は、視準望遠鏡部を回転する回転軸体と、回転軸体に取り付けられた第１の歯車と、第１の歯車に係合する第２の歯車を有する歯車主軸と、歯車主軸を回転可能かつ揺動可能に軸支する球面軸受と、第２の歯車を前記第１の歯車に押付ける押付方向に前記歯車主軸を付勢する付勢部材と、歯車主軸を回転可能に軸支する第１及び第２の軸受と、第１の軸受を押付方向に垂直な一方向に押圧する第１の押圧部材と、第２の軸受を一方向とは逆方向に押圧する第２の押圧部材と、を備えることを特徴とする。 (1) A surveying instrument according to the invention of claim 1 is a rotating shaft body that rotates the collimating telescope unit, a first gear that is attached to the rotating shaft body, and a second gear that is engaged with the first gear. A gear main shaft, a spherical bearing that supports the gear main shaft so as to be rotatable and swingable, and a biasing member that biases the gear main shaft in a pressing direction that presses the second gear against the first gear. The first and second bearings that rotatably support the gear main shaft, the first pressing member that presses the first bearing in one direction perpendicular to the pressing direction, and the second bearing in one direction are And a second pressing member that presses in the reverse direction.

本発明の測量機によれば、第１の押圧部材によって第１の軸受を押付方向に垂直な一方向に押圧し、第２の押圧部材によって第２の軸受を垂直な一方向とは逆方向に押圧するので、垂直な一方向及びその逆方向への歯車主軸の変位を抑え、微動回転駆動の誤差を低減することができる。   According to the surveying instrument of the present invention, the first pressing member presses the first bearing in one direction perpendicular to the pressing direction, and the second pressing member presses the second bearing in the direction opposite to the one vertical direction. Therefore, it is possible to suppress the displacement of the gear main shaft in one vertical direction and in the opposite direction, and to reduce the error of the fine rotation driving.

本発明の実施の形態に係る測量機の外観を模式的に示す正面図である。It is a front view which shows typically the external appearance of the surveying instrument which concerns on embodiment of this invention. 図１に示す測量機の部分破断面を示す概略図である。It is the schematic which shows the partial fracture surface of the surveying instrument shown in FIG. 図１に示す測量機を側面から見た時の部分破断面を示す概略図である。It is the schematic which shows the partial fracture surface when the surveying instrument shown in FIG. 1 is seen from the side. 図３のＩＩ−ＩＩ線に沿う断面図である。但し符号２，１１，１３近傍は理解容易のために、符号１５の中心軸の周りに９０度ずらせて表現している。It is sectional drawing which follows the II-II line | wire of FIG. However, the vicinity of reference numerals 2, 11, and 13 is represented by being shifted 90 degrees around the central axis of reference numeral 15 for easy understanding. 図４の左方の軸支部分（球面軸受）を拡大して示す部分拡大図である。It is the elements on larger scale which expand and show the left axial support part (spherical bearing) of FIG. 図４の右方の軸支部分（玉軸受）を拡大して示す部分拡大図である。It is the elements on larger scale which expand and show the axial support part (ball bearing) of the right side of FIG. 図６のＩＩＩ−ＩＩＩ線に沿う部分断面図である。It is a fragmentary sectional view which follows the III-III line of FIG. 図６のＩＶ−ＩＶ線に沿う部分断面図である。It is a fragmentary sectional view which follows the IV-IV line of FIG. 図２のＩ−Ｉ線に沿う断面図である。It is sectional drawing which follows the II line | wire of FIG. 図９のＶ−Ｖ線に沿う断面図である。但し符号３，１１１，１１２，１１３については理解容易のために、符号１１５の中心軸の周りに９０度ずらせて表現している。It is sectional drawing which follows the VV line of FIG. However, reference numerals 3, 111, 112, and 113 are expressed by being shifted by 90 degrees around the central axis of reference numeral 115 for easy understanding. 実施の形態に係る測量機の構成部品の変形例を模式的に示す部分拡大断面図である。It is a partial expanded sectional view which shows typically the modification of the component of the surveying instrument which concerns on embodiment.

以下、図面を参照しながら本発明の第１の実施の形態による測量機を説明する。
図１は、本発明の一実施の形態による測量機を例示する正面外観図である。測量機１００は、いわゆるトータルステーションと呼ばれる測距測角装置である。測量機１００は、基盤１と、一対の支柱２、２及び台座３を含む装置本体とを備え、一対の支柱２、２は、台座３に対して鉛直軸Ｖの回りに回動可能に支持されている。
一対の支柱２、２には視準望遠鏡部４が水平回転軸Ｈの回りに回動可能に取り付けられている。この視準望遠鏡部４は、目標物（ターゲットなど）を観察するための観察光学系５を有する。なお、測量機１００は、基盤１において不図示の三脚などによって鉛直軸Ｖが鉛直となるように設置される。 Hereinafter, a surveying instrument according to a first embodiment of the present invention will be described with reference to the drawings.
FIG. 1 is a front external view illustrating a surveying instrument according to an embodiment of the present invention. The surveying instrument 100 is a distance measuring and angle measuring device called a so-called total station. The surveying instrument 100 includes a base 1 and an apparatus main body including a pair of support columns 2, 2 and a pedestal 3, and the pair of support columns 2, 2 is supported so as to be rotatable about a vertical axis V with respect to the pedestal 3. Has been.
A collimating telescope unit 4 is attached to the pair of supports 2 and 2 so as to be rotatable about a horizontal rotation axis H. The collimating telescope unit 4 has an observation optical system 5 for observing a target (such as a target). The surveying instrument 100 is installed on the base 1 so that the vertical axis V is vertical by a tripod (not shown) or the like.

測量機１００は、視準望遠鏡部４の向きを上下方向に変えるために視準望遠鏡部４を水平軸Ｈ廻りに微動回転する第１の微動回動機構と、視準望遠鏡部４の向きを左右方向に変えるために、視準望遠鏡部４と支柱２、２とを鉛直軸Ｖ廻りに微動回転する第２の微動回動機構とを備えている。   The surveying instrument 100 changes the direction of the collimating telescope unit 4 and the first fine-movement rotating mechanism that finely rotates the collimating telescope unit 4 about the horizontal axis H in order to change the direction of the collimating telescope unit 4 in the vertical direction. In order to change in the left-right direction, the collimating telescope unit 4 and the columns 2 and 2 are provided with a second fine movement rotating mechanism that finely rotates about the vertical axis V.

第１の微動操作ノブ１１は、視準望遠鏡部４を水平軸Ｈ廻りに微動回転させるための回転操作ノブであり、図１の測量機正面の右側の支柱２に回転可能に取り付けられている。なお、第１の微動操作ノブ１１の設置位置は、図１及び図２に明示したように、右側の支柱２の正面であって、水平軸Ｈから所定距離だけ下方の位置に定められている。
第２の微動操作ノブ１１１は、視準望遠鏡部４と支柱２、２とを一体に鉛直軸Ｖ廻りに微動回転させるための回転操作ノブであり、台座３の側面に回転可能に取り付けられている。 The first fine movement operation knob 11 is a rotation operation knob for finely rotating the collimating telescope unit 4 about the horizontal axis H, and is rotatably attached to the right column 2 on the front of the surveying instrument in FIG. . As shown in FIGS. 1 and 2, the installation position of the first fine movement operation knob 11 is set in front of the right column 2 and a position below the horizontal axis H by a predetermined distance. .
The second fine movement operation knob 111 is a rotation operation knob for finely rotating the collimating telescope unit 4 and the support columns 2 and 2 around the vertical axis V, and is rotatably attached to the side surface of the base 3. Yes.

第１及び第２の微動操作ノブ１１、１１１はそれぞれ、先端部の小径つまみ部１１ａ、１１１ａと大径つまみ部１１ｂ、１１１ｂとを有する。第１の微動操作ノブ１１の小径つまみ部１１ａと大径つまみ部１１ｂとは互いに隣接して一体に形成され、同様に第２の微動操作ノブ１１１の小径つまみ部１１１ａと大径つまみ部１１１ｂとは互いに隣接して一体に形成されている。
操作者は、視準望遠鏡部４を比較的に高速に微動回動したい時には、小径つまみ部１１ａ又は１１１ａを回動操作し、逆に、視準望遠鏡部４を比較的に低速に微動回動したい時には、大径つまみ部１１ｂ又は１１１ｂを回動操作する。 The first and second fine movement operation knobs 11 and 111 have small-diameter knob portions 11a and 111a and large-diameter knob portions 11b and 111b, respectively, at the distal ends. The small diameter knob portion 11a and the large diameter knob portion 11b of the first fine movement operation knob 11 are integrally formed adjacent to each other, and similarly, the small diameter knob portion 111a and the large diameter knob portion 111b of the second fine movement operation knob 111 are formed. Are integrally formed adjacent to each other.
When the operator wants to finely rotate the collimating telescope unit 4 at a relatively high speed, the operator rotates the small-diameter knob unit 11a or 111a, and conversely, the collimating telescope unit 4 is finely rotated at a relatively low speed. When desired, the large-diameter knob portion 11b or 111b is rotated.

先ず、視準望遠鏡部４を水平軸Ｈ廻りに微動回動する第１の微動回動機構の構成を説明する。
図２及び図３において、第１の微動操作ノブ１１のノブ軸１２には、その先端部に平歯車１３が固設されている。この平歯車１３はシザーズギア１４に係合、即ち噛み合っており、このシザーズギア１４は、ウォームギヤ軸１５の一端部に固設されている。
平歯車１３とシザーズギア１４とは、減速機構を構成し、第１の微動操作ノブ１１の回転を減速して、ウォームギヤ軸１５に伝達する。
このウォームギヤ軸１５は、中央部にウォームギヤ１６を有し、他端部において一対の玉軸受１７、１８によって回転可能に軸支されている。この第１及び第２の玉軸受１７、１８は、互いに接近して隣接配置されている。 First, the configuration of the first fine movement rotating mechanism that finely rotates the collimating telescope unit 4 around the horizontal axis H will be described.
2 and 3, a spur gear 13 is fixed to the tip end portion of the knob shaft 12 of the first fine movement operation knob 11. The spur gear 13 is engaged with, or meshed with, the scissors gear 14, and the scissors gear 14 is fixed to one end of the worm gear shaft 15.
The spur gear 13 and the scissor gear 14 constitute a speed reduction mechanism, which reduces the rotation of the first fine movement operation knob 11 and transmits it to the worm gear shaft 15.
The worm gear shaft 15 has a worm gear 16 at the center, and is rotatably supported by a pair of ball bearings 17 and 18 at the other end. The first and second ball bearings 17 and 18 are arranged close to each other and adjacent to each other.

ウォームギヤ１６は、ウォームホイール３０に係合、即ち噛み合っている。このリング形状のウォームホイール３０は、水平回転軸体３１の段差の小径部分に緩嵌、即ち遊嵌され、固定板３２によって水平回転軸体３１に固着されている。この水平回転軸体３１は、その回転によって視準望遠鏡部４を水平軸Ｈの回りに回転駆動する。
また、ウォームギヤ軸１５は、その一端部付近において球面軸受１９によって軸支され、この球面軸受１９は、ウォームギヤ軸１５を、回動可能に支持すると共に球面軸受１９を中心にして揺動可能に支持する。 The worm gear 16 is engaged, that is, meshed with the worm wheel 30. The ring-shaped worm wheel 30 is loosely fitted, that is, loosely fitted to a small-diameter portion of the step of the horizontal rotating shaft body 31, and is fixed to the horizontal rotating shaft body 31 by a fixed plate 32. The horizontal rotary shaft 31 rotates and drives the collimating telescope unit 4 around the horizontal axis H by the rotation.
Further, the worm gear shaft 15 is supported by a spherical bearing 19 in the vicinity of one end thereof, and the spherical bearing 19 supports the worm gear shaft 15 so as to be rotatable and swingable around the spherical bearing 19. To do.

次に、この球面軸受１９の構成及びシザーズギア１４の構成と、両者の関係を詳細に説明する。
図４及び図５において、シザーズギア１４は、互いに隣接したメイン歯車片１４ａとサブ歯車片１４ｂとから構成され、これらのメイン歯車片１４ａとサブ歯車片１４ｂは、平歯車１３と係合したときにバックラッシュを除去するようにバネによってそれぞれ逆方向に付勢されている。
球面軸受１９は、図５に示すように、ウォームギヤ軸１５に形成された凸球面の球面座１９ａと、支柱２に固設されている保持部１９ｂと、この保持部１９ｂに形成された保持凹部１９ｃと、球面座１９ａと保持凹部１９ｃとの間に挟持された複数の小球１９ｄと、から構成される。 Next, the configuration of the spherical bearing 19 and the configuration of the scissors gear 14 and the relationship between them will be described in detail.
4 and 5, the scissor gear 14 is composed of a main gear piece 14 a and a sub gear piece 14 b that are adjacent to each other. When the main gear piece 14 a and the sub gear piece 14 b are engaged with the spur gear 13. Each spring is biased in the opposite direction to remove backlash.
As shown in FIG. 5, the spherical bearing 19 includes a convex spherical spherical surface seat 19a formed on the worm gear shaft 15, a holding portion 19b fixed to the support column 2, and a holding concave portion formed on the holding portion 19b. 19c, and a plurality of small spheres 19d sandwiched between the spherical seat 19a and the holding recess 19c.

球面座１９ａの凸球面の曲率中心Ｏは、ウォームギヤ軸１５の中心線Ｃ上に位置し、かつシザーズギア１４の厚さｄの中心に位置している。なお、この実施の形態にあっては、シザーズギア１４のメイン歯車片１４ａとサブ歯車片１４ｂとは、同一の厚さに構成されているので、球面座１９ａの凸球面の曲率中心Ｏはメイン歯車片１４ａとサブ歯車片１４ｂとの間、即ち両者の連接面位置に位置している。
このようにして、球面軸受１９は、曲率中心Ｏを揺動中心としてウォームギヤ軸１５を揺動可能に軸支している。なお、このウォームギヤ軸１５の揺動角度は±１°程度である。 The center of curvature O of the convex spherical surface of the spherical seat 19 a is located on the center line C of the worm gear shaft 15 and is located at the center of the thickness d of the scissor gear 14. In this embodiment, since the main gear piece 14a and the sub gear piece 14b of the scissors gear 14 are configured to have the same thickness, the curvature center O of the convex spherical surface of the spherical seat 19a is the main gear piece. It is located between the piece 14a and the sub gear piece 14b, that is, at the position of the connecting surface between the two.
In this way, the spherical bearing 19 pivotally supports the worm gear shaft 15 so that the center of curvature O is the center of swinging. The swing angle of the worm gear shaft 15 is about ± 1 °.

ウォームギヤ軸１５には、保持部１９ｂの側面から所定距離だけ離れた位置にフランジ部２０が突設され、このフランジ部２０と保持部１９ｂの側面との間にはドーナツ状の波形バネ２１が設置されている。このドーナツ状の波形バネ２１は、ウォームギヤ軸１５を例えば図４の右方向に付勢している。この波形バネ２１による付勢力により、球面座１９ａは小球１９ｄを介して保持部１９ｂに付勢される。   The worm gear shaft 15 is provided with a flange portion 20 protruding from the side surface of the holding portion 19b by a predetermined distance, and a donut-shaped wave spring 21 is installed between the flange portion 20 and the side surface of the holding portion 19b. Has been. The donut-shaped wave spring 21 urges the worm gear shaft 15 to the right in FIG. 4, for example. Due to the urging force of the wave spring 21, the spherical seat 19a is urged to the holding portion 19b via the small ball 19d.

図３に示すように、ウォームギヤ軸１５の他端と支柱２との間にはコイルバネ２２が張設され、このコイルバネ２２は、ウォームギヤ１６がウォームホイール３０に接近する方向にウォームギヤ軸１５を付勢する。これを更に詳述すると、コイルバネ２２は、ウォームギヤ軸１５が球面座１９ａの凸球面の曲率中心Ｏを中心として揺動傾斜してウォームギヤ１６がウォームホイール３０にバックラッシュを除去するように噛み合うよう、ウォームギヤ軸１５を付勢する。   As shown in FIG. 3, a coil spring 22 is stretched between the other end of the worm gear shaft 15 and the column 2, and this coil spring 22 biases the worm gear shaft 15 in the direction in which the worm gear 16 approaches the worm wheel 30. To do. More specifically, the coil spring 22 is configured so that the worm gear shaft 15 swings and tilts around the center of curvature O of the convex spherical surface of the spherical seat 19a so that the worm gear 16 meshes with the worm wheel 30 so as to remove backlash. The worm gear shaft 15 is biased.

次に、一対の玉軸受１７，１８の機能を詳細に説明する。
図３において、第１及び第２の玉軸受１７、１８の機能は、紙面に平行な上下方向、即ちウォームギヤ軸１５がウォームホイール３０に接近する又は離間する方向へのウォームギヤ軸１５の僅かな移動又は変位を許容するが、その方向に垂直な方向、即ち紙面に垂直な方向へのウォームギヤ軸１５の移動又は変位を阻止することである。 Next, functions of the pair of ball bearings 17 and 18 will be described in detail.
In FIG. 3, the function of the first and second ball bearings 17 and 18 is that the worm gear shaft 15 moves slightly in the vertical direction parallel to the paper surface, that is, the worm gear shaft 15 approaches or separates from the worm wheel 30. Alternatively, the displacement is allowed, but the movement or displacement of the worm gear shaft 15 in the direction perpendicular to the direction, that is, the direction perpendicular to the paper surface is prevented.

図６において、第１及び第２の玉軸受１７、１８はそれぞれ、内輪１７ａ、１８ａと、転動体、即ち玉１７ｂ、１８ｂと、外輪１７ｃ、１８ｃとを有する。内輪１７ａ、１８ａはウォームギヤ軸１５に固設されている。
軸受保持部２５は、支柱２に固設されており、一部に凸状の押圧部２５ａを有する。この凸状押圧部２５ａは、図６及び図７に示すように、第１の玉軸受１７の外輪１７ｃの所定の部分Ｐに当接し、そこを押圧する。この凸状押圧部２５ａの押圧によって第１の玉軸受１７がガタ無く接触し、この部分Ｐにおいて外輪１７ｃと玉１７ｂと内輪１７ａとが互いに密着し、これによって図７において、ウォームギヤ軸１５の矢印Ｄ１方向の変位を実質的に阻止する。なお、この状態においては、Ｐの反対側の玉軸受１７の外輪１７ｃと軸受保持部２５との間には隙間が存在している。 In FIG. 6, the first and second ball bearings 17 and 18 have inner rings 17a and 18a, rolling elements, that is, balls 17b and 18b, and outer rings 17c and 18c, respectively. The inner rings 17 a and 18 a are fixed to the worm gear shaft 15.
The bearing holding portion 25 is fixed to the support column 2 and has a convex pressing portion 25a in part. As shown in FIGS. 6 and 7, the convex pressing portion 25 a abuts on and presses a predetermined portion P of the outer ring 17 c of the first ball bearing 17. The first ball bearing 17 comes into contact with no play by the pressing of the convex pressing portion 25a, and the outer ring 17c, the ball 17b, and the inner ring 17a are brought into close contact with each other in this portion P, whereby the arrow of the worm gear shaft 15 in FIG. The displacement in the D1 direction is substantially prevented. In this state, there is a gap between the outer ring 17 c of the ball bearing 17 on the opposite side of P and the bearing holding portion 25.

図６及び図８に示すように、軸受保持部２５には押圧部材２６が、軸受保持部２５に対して変位可能に取り付けられている。この押圧部材２６は、図示なき付勢部材によって付勢されており、第２の玉軸受１８の外輪１８ｃの所定の部分Ｑに当接して、その部分Ｑを押圧する。外輪１８ｃの所定の部分Ｑは、玉軸受１７の外輪１７ｃの所定の部分Ｐに対して１８０°ずれている。なお、押圧部材２６の押圧力と凸状押圧部２５ａの押圧力とは大きさが等しい。
押圧部材２６の押圧によって第２の玉軸受１８がガタ無く接触し、この部分Ｑにおいて外輪１８ｃと玉１８ｂと内輪１８ａとが互いに密着し、これによって図８において、ウォームギヤ軸１５の矢印Ｄ２方向の変位を実質的に阻止する。なお、この状態においては、Ｑの反対側の玉軸受１８の外輪１８ｃと軸受保持部２５との間には隙間が存在している。 As shown in FIGS. 6 and 8, a pressing member 26 is attached to the bearing holding portion 25 so as to be displaceable with respect to the bearing holding portion 25. The pressing member 26 is urged by an urging member (not shown), abuts against a predetermined portion Q of the outer ring 18 c of the second ball bearing 18, and presses the portion Q. The predetermined portion Q of the outer ring 18 c is shifted from the predetermined portion P of the outer ring 17 c of the ball bearing 17 by 180 °. The pressing force of the pressing member 26 and the pressing force of the convex pressing portion 25a are equal in magnitude.
Due to the pressing of the pressing member 26, the second ball bearing 18 comes into contact with no play, and in this portion Q, the outer ring 18c, the ball 18b and the inner ring 18a are brought into close contact with each other, whereby in FIG. Substantially prevent displacement. In this state, there is a gap between the outer ring 18 c of the ball bearing 18 on the opposite side of Q and the bearing holding portion 25.

なお、上述の説明では、便宜上、凸状押圧部２５ａ及び押圧部材２６がそれぞれ、第１の玉軸受１７及び第２の玉軸受１８を押圧すると説明した。しかしながら、この作用を厳密に説明すると、凸状押圧部２５ａに第１の玉軸受１７を当接した状態で、押圧部材２６を第２の玉軸受１８に押し付けることによって、凸状押圧部２５ａが第１の玉軸受１７に対して反力を及ぼし、これによって凸状押圧部２５ａが見かけ上、第１の玉軸受１７を押圧するというものである。   In the above description, the convex pressing portion 25a and the pressing member 26 are described as pressing the first ball bearing 17 and the second ball bearing 18, respectively, for convenience. However, when this action is strictly explained, the convex pressing portion 25a is pressed by pressing the pressing member 26 against the second ball bearing 18 in a state where the first ball bearing 17 is in contact with the convex pressing portion 25a. A reaction force is exerted on the first ball bearing 17, whereby the convex pressing portion 25 a apparently presses the first ball bearing 17.

このように、図６及び図７において、押圧部２５ａと第１の玉軸受１７とがウォームギヤ軸１５の矢印Ｄ１方向の変位を阻止し、押圧部材２６と第２の玉軸受１８とがウォームギヤ軸１５の逆方向Ｄ２（図８参照）の変位を阻止するので、結局、第１及び第２の玉軸受１７、１８は、ウォームギヤ軸１５を矢印Ｄ１及びＤ２の方向の変位を抑制し、かつＤ１及びＤ２の方向に対して垂直方向に変位可能に支持する。   6 and 7, the pressing portion 25a and the first ball bearing 17 prevent displacement of the worm gear shaft 15 in the direction of the arrow D1, and the pressing member 26 and the second ball bearing 18 are connected to the worm gear shaft. 15, the first and second ball bearings 17 and 18 eventually suppress the displacement of the worm gear shaft 15 in the directions of arrows D1 and D2 and D1. And D2 is supported so as to be displaceable in a direction perpendicular to the direction of D2.

この矢印Ｄ１及びＤ２の方向を図３の紙面に垂直な方向に一致させることによって、第１及び第２の玉軸受１７，１８は、ウォームギヤ軸１５がウォームホイール３０に接近する又は離間する方向へのウォームギヤ軸１５の僅かな移動又は変位を許容するが、その方向に垂直な方向へのウォームギヤ軸１５の移動又は変位を阻止することができる。
また、第１及び第２の玉軸受１７，１８は、ウォームギヤ軸１５の揺動中心、即ち上述の曲率中心Ｏから大きく離れた位置に設置されているので、一層効果的に上述のウォームギヤ軸１５の変位を阻止することができる。 By making the directions of the arrows D1 and D2 coincide with the direction perpendicular to the paper surface of FIG. 3, the first and second ball bearings 17 and 18 move in a direction in which the worm gear shaft 15 approaches or separates from the worm wheel 30. The worm gear shaft 15 can be slightly moved or displaced, but the worm gear shaft 15 can be prevented from moving or displaced in a direction perpendicular to the worm gear shaft 15.
Further, since the first and second ball bearings 17 and 18 are installed at positions far away from the swing center of the worm gear shaft 15, that is, the above-described curvature center O, the above-described worm gear shaft 15 is more effectively provided. Can be prevented.

次に、視準望遠鏡部４を鉛直軸Ｖ回りに微動回動する第２の微動回動機構を説明する。
この第２の微動回動機構は、上述した第１の微動回動機構と実質的に同一構成である。
図９及び図１０において、第２の微動操作ノブ１１１は、台座３の筐体部分に回転可能に取り付けられている。第２の微動操作ノブ１１１のノブ軸１１２にはその先端に平歯車１１３が固設されている。この平歯車１１３はシザーズギア１１４に係合しており、このシザーズギア１１４は、ウォームギヤ軸１１５の一端部に固設されている。 Next, a second fine movement rotating mechanism for finely rotating the collimating telescope unit 4 about the vertical axis V will be described.
The second fine movement rotation mechanism has substantially the same configuration as the first fine movement rotation mechanism described above.
9 and 10, the second fine movement operation knob 111 is rotatably attached to the casing portion of the base 3. A spur gear 113 is fixed to the tip of the knob shaft 112 of the second fine movement operation knob 111. The spur gear 113 is engaged with the scissors gear 114, and the scissors gear 114 is fixed to one end of the worm gear shaft 115.

このウォームギヤ軸１１５は、中央部にウォームギヤ１１６を有し、他端部において一対の玉軸受１１７，１１８によって回転可能に軸支されている。このウォームギヤ１１６は、ウォームホイール１３０に係合、即ち噛み合っている。このリング形状のウォームホイール１３０は、垂直回転軸体１３１の段差の小径部分に緩嵌、即ち遊嵌され、固定板１３２によって垂直回転軸体１３１に固着されている。この垂直回転軸体１３１は、その回転によって、支柱２と視準望遠鏡部４とを一体に鉛直軸Ｖの回りに回転駆動する。
また、ウォームギヤ軸１１５は、その一端部付近において球面軸受１１９によって軸支され、この球面軸受１１９は、ウォームギヤ軸１１５を、回動可能に支持すると共に球面軸受１１９を中心にして揺動可能に軸支する。 The worm gear shaft 115 has a worm gear 116 at the center, and is rotatably supported by a pair of ball bearings 117 and 118 at the other end. The worm gear 116 is engaged with, or meshed with, the worm wheel 130. The ring-shaped worm wheel 130 is loosely fitted, that is, loosely fitted to the small diameter portion of the step of the vertical rotation shaft 131, and is fixed to the vertical rotation shaft 131 by a fixed plate 132. The vertical rotary shaft 131 rotates the column 2 and the collimating telescope unit 4 around the vertical axis V by the rotation.
The worm gear shaft 115 is supported by a spherical bearing 119 in the vicinity of one end of the worm gear shaft 115. The spherical bearing 119 supports the worm gear shaft 115 so as to be pivotable and swingable around the spherical bearing 119. Support.

ウォームギヤ軸１１５にはフランジ部１２０が突設され、このフランジ部１２０と保持部１１９ｂの側面との間にはドーナツ状の波形バネ１２１が設置されている。このドーナツ状の波形バネ１２１は、ウォームギヤ軸１１５を図９の左方向に付勢している。この波形バネ１２１による付勢力は、ウォームギヤ１１６とウォームホイール１３０との間のバックラッシュを除去する。
また、ウォームギヤ軸１１５の他端と台座３との間にはコイルバネ１２２が張設され、このコイルバネ１２２は、ウォームギヤ１１６がウォームホイール１３０に接近する方向にウォームギヤ軸１１５を付勢する。 A flange portion 120 projects from the worm gear shaft 115, and a donut-shaped wave spring 121 is installed between the flange portion 120 and the side surface of the holding portion 119b. The donut-shaped wave spring 121 urges the worm gear shaft 115 in the left direction in FIG. The biasing force by the wave spring 121 removes backlash between the worm gear 116 and the worm wheel 130.
A coil spring 122 is stretched between the other end of the worm gear shaft 115 and the pedestal 3, and the coil spring 122 biases the worm gear shaft 115 in a direction in which the worm gear 116 approaches the worm wheel 130.

次に、上述の実施の形態の動作を以下に説明する。
図１乃至図３において、第１の微動操作ノブ１１を回転操作すると、平歯車１３及びシザーズギア１４によって減速され、ウォームギヤ軸１５に伝達される。
この時、操作者は、第１の微動操作ノブ１１の小径つまみ部１１ａをつまんで操作すると比較的高速で微動操作を行うことができ、大径つまみ部１１ｂをつまんで操作すると比較的低速で微動操作を行うことができる。
ウォームギヤ軸１５の回転は、ウォームギヤ１６とウォームホイール３０とを介して水平回転軸体３１を回動して、視準望遠鏡部４を水平軸Ｈの回りに微動回転駆動する。 Next, the operation of the above embodiment will be described below.
In FIG. 1 to FIG. 3, when the first fine movement operation knob 11 is rotated, it is decelerated by the spur gear 13 and the scissors gear 14 and transmitted to the worm gear shaft 15.
At this time, the operator can perform fine movement operation at a relatively high speed by pinching and operating the small diameter knob portion 11a of the first fine movement operation knob 11, and at a relatively low speed by pinching and operating the large diameter knob portion 11b. Fine movement operation can be performed.
The rotation of the worm gear shaft 15 rotates the horizontal rotary shaft 31 via the worm gear 16 and the worm wheel 30 to finely rotate the collimating telescope unit 4 around the horizontal axis H.

第１の微動操作ノブ１１とウォームギヤ軸１５とは、平歯車１３とシザーズギア１４とによって連結されおり、シザーズギア１４は、平歯車１３との間のバックラッシュを除去するので、第１の微動操作ノブ１１の回転は、遊びの発生無く確実にウォームギヤ軸１５に伝達される。
また、ウォームギヤ軸１５は、波形バネ２１によって軸方向、即ち図３の右方向に付勢され、かつコイルバネ２２によって図３の上方向、即ちウォームホイール３０の方に付勢されている。従って、ウォームギヤ１６とウォームホイール３０とは、バックラッシュの発生無く、常に噛み合い状態を確実に保持するので、ウォームギヤ軸１５の回転は、遊びの発生無く確実にウォームホイール３０に伝達される。 The first fine movement operation knob 11 and the worm gear shaft 15 are connected by a spur gear 13 and a scissor gear 14, and the scissor gear 14 eliminates backlash between the spur gear 13 and therefore the first fine movement operation knob. The rotation of 11 is reliably transmitted to the worm gear shaft 15 without any play.
The worm gear shaft 15 is urged in the axial direction by the wave spring 21, that is, the right direction in FIG. 3, and is urged by the coil spring 22 in the upward direction in FIG. 3, that is, toward the worm wheel 30. Accordingly, the worm gear 16 and the worm wheel 30 always maintain the meshing state without occurrence of backlash, so that the rotation of the worm gear shaft 15 is reliably transmitted to the worm wheel 30 without occurrence of play.

更に、ウォームギヤ軸１５の揺動中心は、球面座１９ａの曲率中心Ｏであり、シザーズギア１４のメイン歯車片１４ａとサブ歯車片１４ｂとの連接面がこの曲率中心Ｏに一致しているので、ウォームギヤ軸１５が揺動し傾斜しても、シザーズギア１４と平歯車１３との間隔変動は最小限に抑えることができる。従って、シザーズギア１４と平歯車１３との噛み合いに対するウォームギヤ軸１５の揺動の影響を実質的に除去することができる。
勿論、シザーズギア１４の厚さ方向の中心、即ち上記連接面と曲率中心Ｏとを完全に一致させなくても、シザーズギア１４の厚さ方向の中心を曲率中心Ｏの近傍に位置することによって、シザーズギア１４と平歯車１３との噛み合いに対するウォームギヤ軸１５の揺動の影響を十分に抑制することができる。 Further, the swing center of the worm gear shaft 15 is the center of curvature O of the spherical seat 19a, and the connecting surface of the main gear piece 14a and the sub gear piece 14b of the scissors gear 14 is coincident with this center of curvature O. Even if the shaft 15 swings and tilts, the variation in the distance between the scissors gear 14 and the spur gear 13 can be minimized. Therefore, the influence of the swing of the worm gear shaft 15 on the meshing between the scissors gear 14 and the spur gear 13 can be substantially eliminated.
Of course, the center of the scissors gear 14 in the thickness direction, that is, the center of the scissors gear 14 in the thickness direction is positioned in the vicinity of the center of curvature O, even if the connecting surface and the center of curvature O do not completely coincide with each other. The influence of the swing of the worm gear shaft 15 on the meshing of the spur gear 14 with the spur gear 13 can be sufficiently suppressed.

第１及び第２の玉軸受１７、１８は、図３において紙面に平行な上下方向へのウォームギヤ軸１５の僅かな変位を許容するが、それに垂直方向への変位を阻止するように、ウォームギヤ軸１５を軸支する。従って、ウォームギヤ１６とウォームホイール３０との紙面に垂直方向の噛み合い箇所は、常に不変、即ち一定であり、このため、ウォームギヤ１６の回転は誤差無く確実にウォームホイール３０に伝達される。
保持部１９ｂは、球面軸受１９の一部を構成すると共に、波形バネ２１を保持する機能を備えるものである。このように保持部１９に複数の機能を持たせることによって、ウォームギヤ軸１５回りの構成のコンパクト化を図ることができる。 The first and second ball bearings 17 and 18 allow a slight displacement of the worm gear shaft 15 in the vertical direction parallel to the paper surface in FIG. 3, but prevent the displacement of the worm gear shaft 15 in the vertical direction. 15 is supported. Accordingly, the meshing position of the worm gear 16 and the worm wheel 30 in the direction perpendicular to the paper surface is always unchanged, that is, constant, so that the rotation of the worm gear 16 is reliably transmitted to the worm wheel 30 without error.
The holding portion 19 b constitutes a part of the spherical bearing 19 and has a function of holding the wave spring 21. Thus, by providing the holding portion 19 with a plurality of functions, the configuration around the worm gear shaft 15 can be made compact.

視準望遠鏡部４を鉛直軸Ｖ回りに微動回動する第２の微動回動機構の動作は、上述の第１の微動回動機構と全く同一であるので、その説明を省略する。   The operation of the second fine movement rotating mechanism that finely rotates the collimating telescope unit 4 about the vertical axis V is the same as that of the above-mentioned first fine movement rotating mechanism, and thus the description thereof is omitted.

上述した玉軸受１７、１８の機構は、凸状の押圧部２５ａが第１の玉軸受１７を介してウォームギヤ軸１５に位置Ｐから外力を加え、他方、押圧部材２６が第２の玉軸受１８を介してウォームギヤ軸１５に位置Ｑから外力を加える構成であるので、ウォームギヤ軸１５にはモーメントが作用し、このモーメントが微動回動機構の動作に悪影響を及ぼす恐れがある。このようなモーメントをできるだけ小さくする為には、第１及び第２の玉軸受１７，１８を互いに近付けて配置すればよいが、それでも、ある程度のモーメントは発生する。   In the above-described mechanism of the ball bearings 17 and 18, the convex pressing portion 25 a applies an external force from the position P to the worm gear shaft 15 via the first ball bearing 17, while the pressing member 26 is the second ball bearing 18. Since an external force is applied from the position Q to the worm gear shaft 15 via a moment, a moment acts on the worm gear shaft 15, and this moment may adversely affect the operation of the fine movement rotating mechanism. In order to make such a moment as small as possible, the first and second ball bearings 17 and 18 may be arranged close to each other, but a certain moment is still generated.

そこで、このようなモーメントの発生を大幅に低減した本発明の別の実施の形態を以下に説明する。
図１１において、第２の玉軸受１８の左右に第１の玉軸受１７と第３の玉軸受１７０とが配置されている。この第３の玉軸受１７０と第２の玉軸受１８との距離は、第１の玉軸受１７と第２の玉軸受１８との距離に等しく定められている。なお、第１及び第２の玉軸受１７、１８は、その構成及び機能が図６の玉軸受１７、１８と同一である。 Therefore, another embodiment of the present invention in which the generation of such moments is greatly reduced will be described below.
In FIG. 11, a first ball bearing 17 and a third ball bearing 170 are arranged on the left and right sides of the second ball bearing 18. The distance between the third ball bearing 170 and the second ball bearing 18 is set equal to the distance between the first ball bearing 17 and the second ball bearing 18. The first and second ball bearings 17 and 18 have the same configuration and function as the ball bearings 17 and 18 in FIG.

軸受保持部２５には、凸状押圧部２５ａに加えて更に第２の凸状押圧部２５ｂが設けられている。この第２の凸状押圧部２５ｂは、位置Ｐ´において第３の玉軸受１７０を押圧する。
第３の玉軸受１７０と第２の凸状押圧部２５ｂは、その構成及び機能が第１の玉軸受１７及び第１の凸状押圧部２５ａの構成及び機能と同一であり、相違点は第１の玉軸受１７と第３の玉軸受１７０とが玉軸受１８を挟むように配置されていることである。
押圧部材２６が第２の玉軸受１８を押圧すると、第１及び第２の凸状押圧部２５ａ、２５ｂにそれぞれ反力が発生し、この反力が第１の玉軸受１７と第３の玉軸受１７０をそれぞれ押圧する。こうして、第１及び第２の凸状押圧部２５ａ、２５ｂの押圧力は、互いに等しく、押圧部材２６の押圧力の半分に等しい。
このような同一構成の第１及び第３の玉軸受１７，１７０を第２の玉軸受１８の左右に配置することによって、図６に示した第１及び第２の玉軸受１７，１８によって発生したモーメントを大幅に低減することができる。 In addition to the convex pressing part 25a, the bearing holding part 25 is further provided with a second convex pressing part 25b. The second convex pressing portion 25b presses the third ball bearing 170 at the position P ′.
The configuration and function of the third ball bearing 170 and the second convex pressing portion 25b are the same as the configuration and function of the first ball bearing 17 and the first convex pressing portion 25a. That is, the first ball bearing 17 and the third ball bearing 170 are arranged so as to sandwich the ball bearing 18.
When the pressing member 26 presses the second ball bearing 18, a reaction force is generated in each of the first and second convex pressing portions 25 a and 25 b, and this reaction force is generated by the first ball bearing 17 and the third ball bearing. Each of the bearings 170 is pressed. Thus, the pressing forces of the first and second convex pressing portions 25a and 25b are equal to each other and equal to half of the pressing force of the pressing member 26.
The first and third ball bearings 17 and 170 having the same configuration are arranged on the left and right sides of the second ball bearing 18 to generate the first and second ball bearings 17 and 18 shown in FIG. Can be greatly reduced.

上述した実施の形態では、ウォームホイール３０を使用したが、これの代わりにヘリカルギアを使用することもできる。
また、シザーズギア１４は、メイン歯車片１４ａの厚さとサブ歯車片１４ｂの厚さが同一であったが、必ずしも、それらの厚さを同一にする必要はなく、メイン歯車片１４ａの厚さとサブ歯車片１４ｂの厚さとを互いに異ならせても良い。この場合には、シザーズギア１４の厚さ方向の中心を球面座１９ａの曲率中心Ｏに一致させるのではなく、メイン歯車片１４ａとサブ歯車片１４ｂとの向かい合った面、即ち連接面を球面座１９ａの曲率中心Ｏに一致させることが望ましい。 In the embodiment described above, the worm wheel 30 is used, but a helical gear can be used instead.
In the scissors gear 14, the thickness of the main gear piece 14a and the thickness of the sub gear piece 14b are the same. However, the thicknesses of the main gear piece 14a and the sub gear are not necessarily the same. The thicknesses of the pieces 14b may be different from each other. In this case, the center of the scissors gear 14 in the thickness direction is not made coincident with the center of curvature O of the spherical seat 19a, but the opposed surfaces of the main gear piece 14a and the sub gear piece 14b, that is, the connecting surfaces are formed on the spherical seat 19a. It is desirable to match with the center of curvature O.

第１の玉軸受１７、第２の玉軸受１８、及び第３の玉軸受１７０は、共通の軸受保持部２５及び押圧部材２６によって、押圧されるが、それぞれ、別個の押圧部材によって押圧してもよい。
また、第１の玉軸受１７と第２の玉軸受１８との間隔は、第２の玉軸受１８と第３の玉軸受１７０との間隔と同一でなくても良く、同様に、第１の玉軸受１７の押圧力と第３の玉軸受１７０の押圧力との和を第２の玉軸受１８の押圧力とを同一にする必要もない。必要なことは、第１の玉軸受１７の押圧力と第２の玉軸受１８の押圧力とによって発生するモーメントを、第２の玉軸受１８の押圧力と第３の玉軸受１７０の押圧力とによって発生するモーメントにほぼ等しくかつ逆向きにすることである。
本発明は、その特徴を損なわない限り、以上説明した実施の形態に何ら限定されない。 The first ball bearing 17, the second ball bearing 18, and the third ball bearing 170 are pressed by the common bearing holding portion 25 and the pressing member 26, but are pressed by separate pressing members, respectively. Also good.
Further, the distance between the first ball bearing 17 and the second ball bearing 18 may not be the same as the distance between the second ball bearing 18 and the third ball bearing 170. It is not necessary to make the sum of the pressing force of the ball bearing 17 and the pressing force of the third ball bearing 170 the same as the pressing force of the second ball bearing 18. What is necessary is that the moment generated by the pressing force of the first ball bearing 17 and the pressing force of the second ball bearing 18 is the same as the pressing force of the second ball bearing 18 and the pressing force of the third ball bearing 170. Is approximately equal to and opposite to the moment generated by.
The present invention is not limited to the embodiments described above as long as the characteristics are not impaired.

１：基盤 ２：支柱
３：台座 ４：視準望遠鏡部
１１：第１の微動操作ノブ １３：平歯車
１４：シザーズギア １５：ウォームギヤ軸
１６：ウォームギヤ １７、１８：玉軸受
１９：球面軸受 ２２：コイルバネ
２５：軸受保持部 ２６：押圧部材
３０：ウォームホイール ３１：水平回転軸体
１００：測量機 １１１：第２の微動操作ノブ
１１３：平歯車 １１４：シザーズギア
１１５：ウォームギヤ軸 １１６：ウォームギヤ
１１７、１１８：玉軸受 １１９：球面軸受
１２２：コイルバネ １３０：ウォームホイール
１３１：垂直回転軸体 Ｈ：水平軸
Ｏ：曲率中心 Ｖ：鉛直軸
1: base 2: support 3: pedestal 4: collimation telescope unit 11: first fine adjustment knob 13: spur gear 14: scissor gear 15: worm gear shaft 16: worm gear 17, 18: ball bearing 19: spherical bearing 22: coil spring 25: Bearing holding portion 26: Pressing member 30: Worm wheel 31: Horizontal rotating shaft body 100: Surveying instrument 111: Second fine movement operation knob 113: Spur gear 114: Scissor gear 115: Worm gear shaft 116: Worm gear 117, 118: Ball Bearing 119: Spherical bearing 122: Coil spring 130: Worm wheel 131: Vertical rotating shaft body H: Horizontal axis O: Center of curvature V: Vertical axis

Claims (8)

視準望遠鏡部を回転する回転軸体と、
前記回転軸体に取り付けられた第１の歯車と、
前記第１の歯車に係合する第２の歯車を有する歯車主軸と、
前記歯車主軸を回転可能かつ揺動可能に軸支する球面軸受と、
前記第２の歯車を前記第１の歯車に押付ける押付方向に前記歯車主軸を付勢する付勢部材と、
前記歯車主軸を回転可能に軸支する第１及び第２の軸受と、
前記第１の軸受を前記押付方向に垂直な一方向に押圧する第１の押圧部材と、
前記第２の軸受を前記一方向とは逆方向に押圧する第２の押圧部材と、
を備えることを特徴とする測量機。 A rotating shaft that rotates the collimating telescope,
A first gear attached to the rotating shaft;
A gear spindle having a second gear engaged with the first gear;
A spherical bearing that pivotally supports the gear spindle so as to be rotatable and swingable;
A biasing member that biases the gear main shaft in a pressing direction for pressing the second gear against the first gear;
First and second bearings that rotatably support the gear main shaft;
A first pressing member that presses the first bearing in one direction perpendicular to the pressing direction;
A second pressing member that presses the second bearing in a direction opposite to the one direction;
A surveying instrument characterized by comprising: 請求項１に記載の測量機において、
前記第１及び第２の軸受は、前記球面軸受から離間した位置において互いに隣接配置されることを特徴とする測量機。 The surveying instrument according to claim 1,
The surveying instrument according to claim 1, wherein the first and second bearings are arranged adjacent to each other at a position separated from the spherical bearing. 請求項２に記載の測量機において、
前記第１の押圧部材の押圧力は、前記第２の押圧部材の押圧力にほぼ等しいことを特徴とする測量機。 The surveying instrument according to claim 2,
The surveying instrument according to claim 1, wherein the pressing force of the first pressing member is substantially equal to the pressing force of the second pressing member. 請求項２に記載の測量機において、
前記歯車主軸を回転可能に軸支する第３の軸受と、
前記第３の軸受を前記垂直な一方向に押圧する第３の押圧部材とを更に備え、
前記第３の軸受は、前記第１の軸受と前記第３の軸受とが前記第２の軸受を挟むように、配置されることを特徴とする測量機。 The surveying instrument according to claim 2,
A third bearing that rotatably supports the gear main shaft;
A third pressing member that presses the third bearing in the vertical direction;
The surveying instrument, wherein the third bearing is disposed such that the first bearing and the third bearing sandwich the second bearing. 請求項４に記載の測量機において、
前記第１の軸受と前記第２の軸受との間隔が前記第２の軸受と前記第３の軸受との間隔にほぼ等しいことを特徴とする測量機。 The surveying instrument according to claim 4, wherein
A surveying instrument characterized in that a distance between the first bearing and the second bearing is substantially equal to a distance between the second bearing and the third bearing. 請求項５に記載の測量機において、
前記第１、第２、及び第３の押圧部材の各々の押圧力は、第１の押圧部材の押圧力と第３の押圧部材の押圧力がほぼ等しく、且つ第１の押圧部材の押圧力と第３の押圧部材の押圧力の和が第２の押圧部材の押圧力にほぼ等しいことを特徴とする測量機。 The surveying instrument according to claim 5, wherein
The pressing force of each of the first, second, and third pressing members is substantially equal to the pressing force of the first pressing member and the pressing force of the third pressing member. And the third pressing member is substantially equal to the pressing force of the second pressing member. 請求項１に記載の測量機において、
前記第１の軸受は、前記歯車主軸に固着された内輪と、前記第１の押圧部材に押圧される外輪と、前記内輪と前記外輪との間に挟持される転動体とを含み、
前記第２の軸受は、前記歯車主軸に固着された内輪と、前記第２の押圧部材に押圧される外輪と、前記内輪と前記外輪との間に挟持される転動体とを含むことを特徴とする測量機。 The surveying instrument according to claim 1,
The first bearing includes an inner ring fixed to the gear main shaft, an outer ring pressed by the first pressing member, and a rolling element sandwiched between the inner ring and the outer ring,
The second bearing includes an inner ring fixed to the gear main shaft, an outer ring pressed by the second pressing member, and a rolling element sandwiched between the inner ring and the outer ring. Surveyor. 請求項４に記載の測量機において、
前記第1の軸受は、前記歯車主軸に固着された内輪と、前記第１の押圧部材に押圧される外輪と、前記内輪と前記外輪との間に挟持される転動体とを含み、
前記第２の軸受は、前記歯車主軸に固着された内輪と、前記第２の押圧部材に押圧される外輪と、前記内輪と前記外輪との間に挟持される転動体とを含み、
前記第３の軸受は、前記歯車主軸に固着された内輪と、前記第３の押圧部材に押圧される外輪と、前記内輪と前記外輪との間に挟持される転動体とを含むことを特徴とする測量機。
The surveying instrument according to claim 4, wherein
The first bearing includes an inner ring fixed to the gear main shaft, an outer ring pressed by the first pressing member, and a rolling element sandwiched between the inner ring and the outer ring,
The second bearing includes an inner ring fixed to the gear main shaft, an outer ring pressed by the second pressing member, and a rolling element sandwiched between the inner ring and the outer ring,
The third bearing includes an inner ring that is fixed to the gear main shaft, an outer ring that is pressed by the third pressing member, and a rolling element that is sandwiched between the inner ring and the outer ring. Surveyor.
JP2009216692A 2009-09-18 2009-09-18 Surveying instrument Active JP5461127B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2009216692A JP5461127B2 (en) 2009-09-18 2009-09-18 Surveying instrument

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2009216692A JP5461127B2 (en) 2009-09-18 2009-09-18 Surveying instrument

Publications (2)

Publication Number Publication Date
JP2011064623A true JP2011064623A (en) 2011-03-31
JP5461127B2 JP5461127B2 (en) 2014-04-02

Family

ID=43951023

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2009216692A Active JP5461127B2 (en) 2009-09-18 2009-09-18 Surveying instrument

Country Status (1)

Country Link
JP (1) JP5461127B2 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104316035A (en) * 2014-11-05 2015-01-28 西安科技大学 Underground traverse survey system, and underground traverse survey method

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0374313U (en) * 1989-11-22 1991-07-25
JP2681221B2 (en) * 1989-08-31 1997-11-26 株式会社トプコン Fine movement device of surveying instrument
JPH10121905A (en) * 1996-10-16 1998-05-12 Mitsubishi Heavy Ind Ltd Rotary shaft support bearing device
JP2001108025A (en) * 1999-10-08 2001-04-20 Koyo Seiko Co Ltd Electric steering device
JP2004203154A (en) * 2002-12-24 2004-07-22 Koyo Seiko Co Ltd Electric power steering device
JP2009097664A (en) * 2007-10-18 2009-05-07 Oiles Ind Co Ltd Bush bearing

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2681221B2 (en) * 1989-08-31 1997-11-26 株式会社トプコン Fine movement device of surveying instrument
JPH0374313U (en) * 1989-11-22 1991-07-25
JPH10121905A (en) * 1996-10-16 1998-05-12 Mitsubishi Heavy Ind Ltd Rotary shaft support bearing device
JP2001108025A (en) * 1999-10-08 2001-04-20 Koyo Seiko Co Ltd Electric steering device
JP2004203154A (en) * 2002-12-24 2004-07-22 Koyo Seiko Co Ltd Electric power steering device
JP2009097664A (en) * 2007-10-18 2009-05-07 Oiles Ind Co Ltd Bush bearing

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104316035A (en) * 2014-11-05 2015-01-28 西安科技大学 Underground traverse survey system, and underground traverse survey method

Also Published As

Publication number Publication date
JP5461127B2 (en) 2014-04-02

Similar Documents

Publication Publication Date Title
JP5908380B2 (en) Power steering device and reduction gear for power steering device
JP6256663B2 (en) Worm reducer
JP5461126B2 (en) Surveying instrument
JP2001163229A (en) Motor-driven steering device
JP2008157351A (en) Reduction gear and vehicular active stabilizer device
JP5461127B2 (en) Surveying instrument
JP2015523274A (en) Adjuster
JP2006281815A (en) Play-filling structure of steering angle ratio variable steering device
JP2007203947A (en) Worm reduction gear for electric power steering device, and electric power steering device with the worm reduction gear built therein
JP2006150994A (en) Variable steering angle mechanism using differential gear device
JPH09193815A (en) Electric power steering device
JP2681221B2 (en) Fine movement device of surveying instrument
JP2009208612A (en) Variable steering angle ratio steering device for vehicle
JP2010043744A (en) Joint structure, reduction gear mechanism and steering assisting device using the same
JP2010039351A (en) Structure for adjusting operation balance of gimbal of space stabilizing device
JP2005054860A (en) Worm gear device
JP5120626B2 (en) Dial operation device
JP2021172232A (en) Steering gear
CN104321561B (en) Anchor ring drives the scroll wheel positions in CVT to control
JPH11230749A (en) Surveying instrument
JP2010106996A (en) Transmission and measuring machine
JP2004360809A (en) Gear with torque limiter and power transmitting mechanism of electronic apparatus
JP2004175239A (en) Transmission device and electric power steering device equipped therewith
JP2785047B2 (en) Fine movement device of surveying instrument
JP2002225734A (en) Electric power steering device

Legal Events

Date Code Title Description
A625 Written request for application examination (by other person)

Free format text: JAPANESE INTERMEDIATE CODE: A625

Effective date: 20120502

A977 Report on retrieval

Free format text: JAPANESE INTERMEDIATE CODE: A971007

Effective date: 20130424

A131 Notification of reasons for refusal

Free format text: JAPANESE INTERMEDIATE CODE: A131

Effective date: 20130430

A521 Request for written amendment filed

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20130624

TRDD Decision of grant or rejection written
A01 Written decision to grant a patent or to grant a registration (utility model)

Free format text: JAPANESE INTERMEDIATE CODE: A01

Effective date: 20131217

A61 First payment of annual fees (during grant procedure)

Free format text: JAPANESE INTERMEDIATE CODE: A61

Effective date: 20140115

R150 Certificate of patent or registration of utility model

Ref document number: 5461127

Country of ref document: JP

Free format text: JAPANESE INTERMEDIATE CODE: R150

Free format text: JAPANESE INTERMEDIATE CODE: R150

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250