JP2006266393A - Rotary shaft connection mechanism - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a rotary connection mechanism capable of connecting three shafts mutually, causing an error in at least one shaft at assembly time, causing angle of deviation and eccentricity of axis among each shaft due to the error, preventing occurrence of resonance, abnormal vibration, and abnormal metallic sound, and facilitating connection among each shaft. <P>SOLUTION: This rotary shaft connection mechanism for connecting the first and second rotary shafts 100 and 200 whose central lines are not on the same straight line always mutually is provided with a universal coupling J1 constituted to make backlash zero, the third rotary shaft (movable shaft) 300 connected with the universal coupling J1 and the first rotary shaft 100, and an aligning mechanism 1 for supporting the third rotary shaft (movable shaft) 300. The aligning mechanism 1 is constituted to position the third rotary shaft (movable shaft) 300 for either of the first and second rotary shafts 100, 200 accurately and fix the third rotary shaft (movable shaft) 300 so as to rotate it, but to prevent occurrence of whirling. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a rotary connection mechanism in which three shafts are connected to each other, and at least one shaft has an error during assembly and the like, and an error or eccentricity occurs between the shafts due to the error or the like. .

  For example, a test that measures whether an engine is fulfilling its final function by actually running the engine and absorbing the output of the engine using a power absorbing rotating body connected to the engine output shaft. There is a way.

  However, in such a test method, vibration and noise are generated when the fuel is actually supplied and the engine is operated. In order to prevent the noise, a test room that is specially sound-insulated and sound-absorbed is required.

In order to avoid the generation of noise, there is a motoring test method in which fuel is not supplied to the engine, an electric motor is connected to the output shaft of the engine, the engine is rotated, and vibrations of the engine are analyzed.
FIG. 13 and FIG. 14 are diagrams showing a simplified state of such a motoring test method.

  In FIG. 13, the engine E is supported by the support members 1 </ b> J and 2 </ b> J standing on the foundation G via the automatic clamp C. A first transmission shaft 5J is fixedly connected to the output shaft 4J of the engine E, and is connected to a shaft 7J on the motor 6J side by a joint 8J.

Here, a cross section (Z-Z cross section of FIG. 13) of the support member 1J (engine rear mount) is shown in FIG. In FIG. 15, the center point of the original engine when the engine is supported by the support member 1J is P1. The surface 1Ja for mounting the engine E of the support member 1J and the corresponding mounting surface Ea on the side of the engine E are generally formed by inclined surfaces.
For the test, when the engine E is supported on the support member 1J, the engine E is suspended from above the support member 1J by, for example, a simple crane (not shown) and placed on the support member 1J.
After the engine E is placed on the support member 1J, the engine E and the support member 1J are fixed by the automatic clamp C.
When the engine E is mounted on the support member 1J, the engine E is suspended by a simple crane or the like, and thus a slight shift occurs in the left-right direction despite sufficient attention. In addition, since the mounting surfaces Ea and 1Ja are inclined, not only the horizontal displacement but also the height H direction from the base G of the original engine center point P1 (the dimension H is the planned normal engine height). Shift) occurs.
Point P2 indicates the engine center point deviated from the original position. That is, in the drawing, a deviation of h in the height direction and δ in the left-right direction is generated.

  FIG. 13 shows a case where the deviation angle θ has occurred in the joint 8J because such a shift has occurred. In the state of FIG. 13, since the connecting shaft 5J and the shaft 7J on the motor 6J side intersect at the center of the joint 8J, which is the original intersection, only the declination angle θ is generated. A type without backlash can be used.

  However, as shown in FIG. 14, not only the deflection angle at the center of the joint 8J but also the eccentricity λ (the deviation in the height direction is shown in FIG. If a type without backlash is used in such a case, the deflection angle θ and the eccentricity λ cause a swing around the connecting shaft side (transmission shaft rampage). In addition to the connection parts and / or the support members, the soot stock may damage the engine and the motor. In other words, if the mounting position of the engine E shifts even a little, the power transmission type will resonate and abnormal vibration will occur, which will not only prevent the collection of accurate test data, but will also cause serious damage to the entire test equipment. It could have been.

  In order to avoid such an abnormal situation, it is necessary to create a special large positioning jig for mounting the test equipment and the engine which is the test object. In such a case, the test cost is greatly increased. End up.

Other than the above, the cable mounted on the foundation movably and the driving device fixed on the foundation between the two opposing wall surfaces of the table, and the movably arranged on both sides of the driving device. And two movable parts fixed to the two wall surfaces, a chamber formed in the axial direction between the movable part and the driving device, and a hydraulic pressure supply system for supplying hydraulic pressure to the chambers Has been proposed (see, for example, Patent Document 1). However, this proposal is aimed at enhancing the responsiveness and exhibiting good characteristics, and does not solve the above-mentioned problems.
JP-A-11-65154

  The present invention has been proposed in view of the above-described problems of the prior art. Three shafts are connected to each other, and at least one shaft has an error during assembly, and the like. An object of the present invention is to provide a rotary connection mechanism that does not generate resonance, abnormal vibration, and abnormal metal sound, and that can be easily connected between the axes.

  The rotary connection mechanism of the present invention is configured such that the backlash is zero in the rotary shaft connection mechanism that connects the first (100) and the second rotary shaft (200) whose center lines are not necessarily on the same straight line. A universal coupling J1, a third rotational axis (movable axis 300) connected to the universal coupling J1 and connected to the first rotational axis (100), and a third rotational axis (movable axis 300). A centering mechanism (1) that supports the shaft, and the centering mechanism (1) is configured so that the third rotating shaft (movable 300) is one of the first (100) and the second rotating shaft (200). The third rotation shaft (movable shaft 300) can be rotated but can be fixed so as not to swing around while being configured so that it can be accurately positioned with respect to one of the rotation shafts. (Claim 1).

  The alignment mechanism (1) supports the third rotation shaft (movable shaft 300) and extends in the vertical direction or the horizontal direction perpendicular to the axis of the third rotation shaft (300) and is coaxial. A bearing (10) having a pair of first rods (15) arranged, and the first rod (15) of the bearing (10) is pivoted by a first bearing hole (inner diameter portion of the sleeve 24). A pair of second rods (23) arranged on the same axis and extending in a direction orthogonal to the pair of rods (15) perpendicular to the axis of the supporting third rotating shaft (movable shaft 300). And a frame (30) for pivotally supporting the second rod (23) of the casing (20) by a second bearing hole (inner diameter portion of the sleeve 38). The first rod (15) is slidable and rotatable in the first bearing hole (inner diameter portion of the sleeve 24). To be configured, the second rod (23) is configured within the second bearing hole (inner diameter of the sleeve 38) and rotatably slidable (claim 2).

  A fixing member for fixing the first (15) and / or the second rod (23) to the first bearing hole (inner diameter portion of the sleeve 24) and the second bearing hole (inner diameter portion of the sleeve 38). And the members 24, 38 and the mechanisms 24, 38, etc. for supplying hydraulic pressure to the sealed space formed by the outer peripheries of the sleeves 24, 38 and the stepped through holes 22b, 32a into which the sleeves 24, 38 are inserted. And fixing the first (15) and / or the second rod (23) with the fixing member to position the bearing (10) in the casing (20) and the frame (30). When the position of the casing (20) is determined and the fixing member is in the unlocked state, the first (15) and / or the second rod (23) is the first (inner diameter portion of the sleeve 24) and / or Or second Shaft hole and slidable inside (inner diameter of the sleeve 38) is rotatably configured (claim 3).

  Of the first (15) and second rod (23), the lower end of the rod (15) extending in the downward direction of the bearing (10) and the first (inner diameter portion of the sleeve 24) and second Between the bearing hole (inner diameter portion of the sleeve 38) and the reference surface (the inner bottom surface of the cap 26) that forms the bottom of the bearing hole (inner diameter portion of the sleeve 24) extending in the downward direction of the bearing. An elastic member (original position return spring S1) biased in a direction against the mass of the bearing (10) or casing (20) of the alignment mechanism (1) and having an elastic repulsive force substantially equal to the mass is interposed. (Claim 4).

  At the ends of the first (15) and second rod (23), an elastic member (original) that biases the rod (15, 23) in the axial direction of the third rotation shaft (movable shaft 300). Position return springs S2, S4, S4) are interposed (Claim 5).

  The first rotary shaft is an engine output shaft system or a rotary shaft (100) connected to the engine output shaft system, and the second rotary shaft is a shaft (200) connected to the output shaft of the electric motor. The third rotation shaft (movable shaft 300) is directly connected to the engine output shaft system via the transmission plate (9) or via the transmission plate 9 via the first rotation shaft (100). Are connected to the output shaft system (flywheel 82).

  The transmission plate (9) is fixed to the third rotating shaft (movable shaft 300) side, and a pin (P) is fixed on the same axis as the third rotating shaft (300). ) Is axially supported by a bearing (83) provided on the output side (82) of the engine so that it is aligned with the output shaft (81) of the engine (claim 7).

  According to the present invention having the above-described configuration, the alignment mechanism (1) supports the third rotating shaft (movable shaft 300) and is perpendicular to the axis of the third rotating shaft (300). A bearing (10) having a pair of first rods (15) extending in a direction or a horizontal direction and arranged coaxially, and the first rod (15) of the bearing (10) is a first By the casing (20) pivotally supported by the bearing hole (inner diameter portion of the sleeve 24), first, the first rod (15) is linearly moved in the extending direction and rotated around the first rod (15). Two degrees of freedom are secured.

  Further, the casing (20) extends in a direction orthogonal to the pair of rods (15) perpendicular to the axis of the third rotating shaft (movable shaft 300), and is disposed on the same axis. Two rods (23), and the second rod (23) is pivotally supported by the second bearing hole (inner diameter portion of the sleeve 38) of the frame (30), thereby Two degrees of freedom of the straight movement in the extending direction of the rod (23) and the rotation around the second rod (23) are ensured.

As a matter of course, all the rotation axes including the movable axis (300) do not change the length in the axial direction, and are free in all of the 6 degrees of freedom except the universal dimension (the dimension in the extending direction of the axis). A degree (4 degrees of freedom) is secured.
That is, by interposing the alignment mechanism (1) including the third axis (movable axis 300) between the first (100) and the second rotation axis (200), the first (100) and the first axis When connecting the two rotation shafts (200), if the center lines of these rotation shafts are not on the same straight line, or if they do not coincide, four degrees of freedom are secured. Even if it exists, the intersection of adjacent rotating shafts can be made to coincide with the center of the joint (free joint).
If the intersecting point of each axis coincides with the center point of the joint, the rotation of the rotating shaft (movable shaft 300), which has been a concern in the past, the abnormal vibration associated therewith, the generation of sound, etc. will not occur, and the backlash is zero. It is possible to use a joint (a universal joint) configured to be Since the backlash is zero, the measurement accuracy of the engine is significantly improved.

  Of the first (15) and second rod (23), the lower end of the rod (15) extending in the downward direction of the bearing (10) and the first (inner diameter portion of the sleeve 24) and second Of the bearing hole (inner diameter portion of the sleeve 38), and a reference surface (inner bottom surface of the cap 26) that forms the bottom of the bearing hole (inner diameter portion of the sleeve 24) extending in the downward direction of the bearing, An elastic member (original position return spring S1) biased in a direction against the mass of the bearing (10) or casing (20) of the alignment mechanism (1) and having an elastic repulsive force substantially equal to the mass is interposed. Therefore, a large force is not required for assembling the rotating shaft.

  Furthermore, at the end portions of the first (15) and the second rod (23), an elastic member (which urges the rod (15, 23) in the axial direction of the third rotating shaft (movable shaft 300)). Since the position return springs S2, S4, S4) are interposed, alignment is easy. Alternatively, this also contributes to automatic alignment of the movable shaft (300) after assembly.

  The transmission plate (9) is fixed to the third rotating shaft (movable shaft 300) side, and a pin (P) is fixed on the same axis as the third rotating shaft (300). Is supported by a bearing (83) provided on the output side (82) of the engine so that it can be easily aligned with the output shaft (81) of the engine.

Embodiments of the present invention will be described below with reference to the accompanying drawings.
In the accompanying drawings, the same portions and the same components are denoted by the same reference numerals, and the description of the reference symbols is avoided.

First, the configuration of the entire motoring test apparatus according to the embodiment will be described with reference to FIG.
In FIG. 1, a motoring test apparatus MT includes an alignment mechanism 1, an inverter motor 2, a power transmission belt 3 and a speed reducer 4 that constitute a speed change mechanism, and a torque detector 5 that measures driving torque of the power transmission system. The flywheel 6 for suppressing rotation unevenness and the flywheel bearing 7 that supports the flywheel 6 are provided.
In the figure, reference numeral 8 denotes an engine which is an object to be measured.

  The flywheel 6 is fixed by a tapered portion 62 of a flywheel shaft 60, and the flywheel shaft 60 is rotatably supported by the flywheel bearing 7.

  The rotation of the inverter motor 2 is transmitted to the speed reducer 4 by the driving force transmission belt 3.

  The output shaft 41 of the speed reducer 4 is connected to one end 51 of the rotating shaft of the torque detector 5 via a pair of universal joints J and J and a transmission shaft S45 between the universal joints J and J.

  The other end 52 of the rotating shaft of the torque detector 5 is connected to one end 61 of the flywheel shaft 60 via a pair of universal joints J, J and a transmission shaft S56 between the universal joints J, J. ing.

  Here, referring also to FIG. 3 (detailed view of B part in FIG. 1), the alignment mechanism 1 is pivotally supported by a bearing 10 described later, and the alignment mechanism 1 is moved up and down within a predetermined range by a method described later. It has a movable shaft 300 (a third rotating shaft in the claims) that is movable in the left-right direction (the front-back direction of the paper surface in FIG. 1).

  As shown in detail in FIG. 4 (detailed view of part C in FIG. 3), the engine flywheel 82 is fixed to the output shaft 81 of the engine 8 with bolts B1, and the transmission plate 9 is shown on the flywheel 82. It is attached with mounting bolts that do not.

  In the illustrated example, the transmission plate 9 includes a disc-shaped member 91 having an insertion hole 91a formed in the center thereof, and a central member 92 having a cup-like shape and an annular flange 92f at the maximum diameter portion, integrally formed by a bolt B2. ing. An outer bottom portion 92a of the central member 92 protrudes in a cylindrical shape, and a circular recess 92b is formed at the center of the outer bottom portion 92a. Further, a stepped bolt insertion hole 92d is formed so as to penetrate from the inner bottom 92c to the outer bottom 92a of the central member 92.

A guide pin P is fitted into the recess 92b, and the guide pin P is fixed to the central member 92 by a mounting bolt B3 inserted from the inner bottom portion 92c.
The guide pin P is inserted into the inner race of the inner race of the bearing 83 that pivotally supports the tip of the main drive shaft of the transmission (not shown) attached to the center of the clutch plate 82 so that the guide pin P can be smoothly inserted without play. The diameter is set.

  Referring again to FIG. 3, the transmission plate 9 and the movable shaft 300 are connected by a first extending rotary shaft (first rotary shaft in the claims) 100. In the first extending rotary shaft 100, one end of the pipe-shaped shaft portion 110 is a cylindrical end portion 120, a circular flange 130 is formed in the vicinity thereof, and a circular flange 140 is formed at the other end portion. Is formed. The cylindrical end portion 120 is configured to be fitted to the cup-shaped inner diameter portion 92e of the central member 92 of the transmission plate 9 (see FIG. 4).

  3 and 1, the movable shaft 300 is connected to a flange 220 of a second extending rotary shaft (second rotary shaft in claims) 200 through a universal coupling J1 without backlash. . The second extending rotary shaft 200 is constituted by a pipe-shaped shaft portion 210 and flanges 220 formed at both ends thereof. The remaining flange 220 of the second extending rotary shaft 200 is connected to the end portion 63 on the tapered portion 62 side of the shaft 60 of the motor-side flywheel 6 via the same free coupling J1 as described above. The In order to fix the flywheel 6 to the tapered portion 62 of the shaft 60, a lock nut N that is screwed into a male screw portion 64 formed adjacent to the tapered portion 62 is tightened.

Here, FIG. 2 schematically shows the AA cross section of FIG. 1, and is a diagram for simply explaining the relative movement of the movable shaft 300 with respect to the foundation G. FIG.
The alignment mechanism 1 allows the bearing 10 that supports the movable shaft 300 and rotation of the bearing 10 around the vertical axis V (movement of the arrow R1) and slides along the vertical axis V (arrow Y1). 3) of the casing 20 to be moved around the horizontal axis H (movement of the arrow R2), and the frame body 30 to be slid slightly along the horizontal axis H (movement of the arrow Y2). It consists of two major components.
Reference numerals S1, S2, and S4 (all springs) in FIG. 2 will be described later with reference to FIGS.

  5 and 6 are a side view and a front view showing the overall configuration of the alignment mechanism 1. FIG. In FIGS. 5 and 6, reference numeral S <b> 1 is a spring for returning to the original position when the bearing 10 is moved downward and is mounted below the casing 20, and the mass of the entire bearing 10 in a state where the movable shaft 300 is supported. In addition, a predetermined force is applied vertically upward.

  Reference numeral S2 is also mounted above the casing 20, and since the original position return spring S1 is biased too much, the adjustment screw N1 screwed into the bias adjustment rod 16 described later is screwed in, It is an adjustment spring for reducing excessive bias.

  Reference numeral S3 is also attached to the left and right of the front of the casing 20 (right side in FIG. 5) and is a spring for returning the original position to the left and right rotation of the bearing 10. The biasing can be adjusted by screwing an adjusting bolt (not shown).

  Reference numeral S4 is provided at each of the left and right end portions of the frame 30 and is a spring for returning the original position to the left and right movement of the casing 20, and is screwed in an adjusting screw N2 screwed to an urging adjustment rod 27 described later. You can adjust the bias.

  Reference numeral S <b> 5 is a spring for returning to the original position with respect to movement and rotation of the bearing 10 in the front-rear direction, which is also mounted on the front and rear above the frame 30. The biasing can be adjusted by screwing the adjusting bolt B50.

  The casing 20 that supports the bearing 10 has a considerable mass. Therefore, reference numeral S6 is an adjustment spring equipped to lift the bearing 230 from below in order to facilitate the rotation of the second rod 23 described later of the casing 20 and the sliding in the rod axis direction. The adjustment mechanism including this adjustment spring will be described in detail in the description of the frame body 30.

  5 and 6, reference B <b> 60 indicates an adjustment bolt used when adjusting the bias of the adjustment spring S <b> 6, and reference numeral 310 indicates an end flange of the movable shaft 300. Reference numeral 17 denotes a spring seat of the return spring S2, reference numeral 28 denotes a spring seat of the return spring S4, reference numeral SS denotes a spring seat of the return spring S1, and reference numeral 230C denotes a bearing case described later.

Next, with reference to FIG.7 and FIG.8, the detailed structure of the bearing 10 is demonstrated.
7 and 8, the bearing 10 that supports the movable shaft 300 includes a central box-like body 11 having a pair of bearings 12 attached thereto, and an upper rod connection that is attached above the box-like body 11 by a bolt B4. A member 13 and a lower rod connecting member 14 attached with a bolt B4 below the box-like body 11 are provided.

  The upper rod connecting member 13 and the lower rod connecting member 14 are respectively formed with rod insertion holes 13a and 14a penetrating in the vertical direction in the drawing. The rod insertion holes 13 a and 14 a are fitted with the columnar end 15 c of the first rod 15 having the flange portion 15 b in the middle of the columnar member 15 a, and are inserted into the upper rod connecting member 13 and the lower rod connecting member 14. Each is fixed with a mounting bolt B5.

  Here, the flange 15b of the first rod 15 has a surface F facing the object to be measured (engine 8) that coincides with the end surface in the same direction of the upper rod connecting member 13, and the surface F of the flange 15b is on the surface F. A positioning hole 18 for determining the original position is formed. By inserting a positioning pin 19 through which a positioning hole (33Aa; which will be described later) formed in a frame 30 described later is inserted into the positioning hole 18, the bearing 10, that is, the movable shaft 300, is the original in the alignment mechanism 1. (See FIG. 5).

  An urging adjustment rod 16 is embedded at the top of the upper first rod 15, and a male screw 16 a is formed from the tip of the urging adjustment rod 16 downward. The spring S21 for returning the original position is set on the male screw 16a, and an adjustment nut N1 is screwed through the spring seat 17 (see FIGS. 5 and 6).

  The lower rod connecting member 14 is formed longer than the upper rod connecting member 13 from the vertical axis V10 in FIG. 7 (to the right in FIG. 7). The vicinity of the long rear end 14b is a portion where the end face of the return spring S3 for returning the left-right rotation of the bearing 10 to the original position contacts.

A large through hole 11c is formed on the side surface of the box-like body 11 for the purpose of weight reduction (see FIG. 7), a stepped through hole 11a having three steps is formed on the front surface, and a bearing 12 is provided in the medium diameter hole. It is installed. Further, a stepped (two-step) through hole 11b is formed on the rear surface, and a bearing 12 is mounted on the large diameter portion thereof. The front bearing 12 prevents the bearing from deviating by a stop ring 12C.
In FIG. 8, the two-dot line indicates the flange (310; see FIG. 5) of the movable shaft 300.

Next, the detailed configuration of the casing 20 will be described with reference to FIGS. 9 and 10.
9 and 10, in the casing 20, left and right vertical members 21 and 21 and upper and lower horizontal members 22 and 22 are coupled in a cross beam shape with fastening bolts B6.

  Each vertical member 21 is formed with a stepped rod insertion hole 21a penetrating in the horizontal direction in FIG. The rod insertion holes 21a are fitted with the columnar end portions 23c of the second rod 23 having the flange portions 23b in the middle of the columnar member 23a, and are fixed to the vertical members 21 with mounting bolts B7.

Further, each vertical member 21 is formed with a rectangular projection 21b below the center in the vertical direction in FIG. 9, and this projection 21b is provided with a through-hole 21c penetrating the member 21 in the horizontal direction. A spring S3 for returning the original position of the left and right rotation of the bearing 10 is stored in the through hole 21c (see FIGS. 5 and 6).
The spring S3 is configured such that the biasing can be adjusted by means (not shown).
In addition, the vertical / front / rear direction positions of the protrusion 21b in the entire alignment mechanism 1 coincide with the rear end 14b of which the rear part is formed long from the vertical axis V10 in FIG.

  A blind hole 29 into which a positioning pin is inserted in order to determine the original position is formed on either the left or right side of the vertical member 21 with the opening facing outward in the left-right direction.

  Each horizontal member 22 is formed with a notch step portion 22a such that the center side in the left-right direction moves away from the center in the vertical direction. The notch step portion 22a is formed to escape the flange portion 15b of the first rod 15 of the bearing 10 when the first rod 15 of the bearing 10 moves in the vertical direction.

  Further, in the center of the horizontal member 22 in the left-right direction and the front-rear direction, a stepped through hole 22b having a large diameter portion, a medium diameter portion, and a small diameter portion is formed, and the large diameter portion and the medium diameter of the through hole 22b are formed. The sleeve 24 with the flange is mounted so as to be embedded over the portion, and is fixed to the horizontal member 22 with a fixing bolt B8. The inner diameter of the sleeve 24 and the inner diameter of the small diameter portion of the stepped through hole 22b are formed to have the same size, and the first rod 15 of the bearing 10 is smoothly slid.

  The sleeve 24 includes a cylindrical portion 24a and a flange 24b. A hollow 24c is formed on the outer periphery of the cylindrical portion 24a over the entire circumference, and a sealed space is formed between the intermediate diameter portion of the stepped through hole 22b. Is formed.

An oil supply port 24i is formed on the through hole 22b side of the sealed space, and the oil supply port 24i is connected to the pipings Li3 and Li4 of the hydraulic pressure supply line composed of the pipings Li1 to Li4.
A return line Lo branches off from a branch point B1 between the pipes Li1 and Li2 of the hydraulic pressure supply line, and an end thereof is connected to the oil tank 600. A hydraulic pump 500 is interposed in the piping Li1 of the hydraulic supply line, and a flow rate control valve 700 is interposed in the piping Li2. On the other hand, an open / close valve 750 is interposed in the hydraulic pressure discharge line Lo.
Although the hydraulic pump 500, the oil tank 600, and the flow rate adjusting valve 700 are illustrated as being provided inside the casing, these are provided outside the alignment mechanism 1.
A symbol B2 in FIG. 10 indicates a (second) branch point of the hydraulic pressure supply line.

In the sleeve 24 configured as described above, the on-off valve 750 is closed, the opening degree of the flow rate adjusting valve 700 is adjusted, the hydraulic pump 500 is operated, and compressed oil is supplied to the sealed space. The movement of the first rod 15 in the vertical direction and the rotational direction can be restricted. In other words, the movable shaft 300 is temporarily fixed at an arbitrary position, and the connection work with the counterpart rotating shaft to be connected to the movable shaft 300 can be facilitated.
On the other hand, in order to loosen the restriction in the vertical direction and the rotation direction of the first rod 15, the hydraulic pressure on the sleeve side is lowered by stopping the hydraulic pump 500 and opening the on-off valve 750, and the restriction by the hydraulic pressure of the movable shaft 300 can be released. .
In order to simplify the entire apparatus, it is possible to omit the hydraulic circuit and the sealed space as described above (use of a sleeve without a depression).

  A cap 25 is attached to the center of the top of the upper member of the horizontal member 22. The cap 25 is formed with a relief hole 25a of the first rod 15 of the bearing 10 having the same diameter as the small diameter portion of the three stepped through holes 22b and disposed at the same position as the small diameter portion. The upper outside of the cap 25 is formed with an insertion hole 25b through which the urging adjustment rod 16 is inserted.

  On the other hand, a cap 26 is attached to the center of the bottom of the lower member of the horizontal member 22. The cap 26 is formed with a relief hole (blind hole) 26a of the first rod 15 of the bearing 10 having the same diameter as that of the small diameter portion of the three stepped through hole 22b and the same position as the small diameter portion. Yes. The spring S1 for returning the original position when the bearing 10 moves downward is stored in the escape hole 26a via the spring seat SS (see FIG. 6).

  An urging adjustment rod 27 is embedded at the outer ends of the left and right second rods 23, and a male screw 27 a is formed from the tip of the urging adjustment rod 27 toward the center of the casing 20. Yes. The spring S4 for returning the original position is set on the male screw 27a, and the adjustment nut N2 is screwed through the spring seat 28 (see FIGS. 5 and 6).

  Next, the detailed configuration of the frame 30 will be described with reference to FIGS. 11 and 12. In FIG. 12, the frame body 30 has vertical members 32, 32 erected on the left and right substrates 31, 31, and the left and right vertical members 32, 32 in a cross-beam shape on the front and rear surfaces of the upper ends of the vertical members 32, 32. It has the horizontal member 33A (engine 8 side) and 33B (motor 2 side) to connect, and the foundation 34 which connects the board | substrates 31 and 31 on either side with the fastening bolt B9 in the lower surface.

  A positioning through hole 33Aa for inserting and penetrating the positioning pin 19 is formed at the center of the horizontal member 33A near the lower edge.

  Near the upper and lower centers of the vertical members 32 and 32, bearing portions 35 and 35 are formed on the left and right outer sides, and caps 36 and 36 are formed on the outer sides thereof. Referring also to FIG. 11, reinforcing ribs 37 </ b> A (above the bearing portion 35) and 37 </ b> B (below the bearing portion 35) are formed on the left and right outer surfaces of the vertical members 32, 32 so as to contact the bearing portion 35. Has been.

  Stepped through holes 32 a and 32 a are formed over the vertical member 32 and the bearing portion 35 so that the center of the hole passes through the centers of the front and rear and upper and lower sides of the bearing portion 35. A flanged sleeve 38 is embedded in the stepped through holes 32a over the entire length, and is fixed to the vertical member 32 with fixing bolts B10.

  On the other hand, a hole 36a having a larger diameter than the small diameter portion of the stepped through hole 32a (a storage hole of a bearing case 230C described later) 36a is formed on the side of the cap 36 that is in contact with the bearing portion 35, and the outer side adjacent to the hole 36a. A relief hole 36b (a hole through which the second rod 23 of the casing 20 escapes when sliding in the sleeve) is formed concentrically with the inner diameter of the sleeve 38. Further, an insertion hole 36c through which the urging adjustment rod 27 of the casing 20 is inserted is formed on the outer side of the escape hole 36b and on the outer side of the escape hole 36b and the cap 36.

  Here, the sleeve 38 has a cylindrical portion and a flange similar to the sleeve 24 of the casing 20 described above, and a recess is formed in the outer periphery of the cylindrical portion over the entire periphery, and the stepped through hole 32a. A sealed space is formed with the middle diameter portion.

As in the case of the casing 20, an oil supply port 38i is formed on the through hole 32a side of the sealed space, and the oil supply port 38i is connected to the pipes Li6 and Li7 of the hydraulic pressure supply line made of the pipes Li1, Li5 to Li6. Yes.
A return line Lo branches from a branch point B1 between the pipings Li1 and Li5 of the hydraulic pressure supply line, and an end thereof is connected to the oil tank 600. A hydraulic pump 500 is interposed in the piping Li1 of the hydraulic supply line, and a flow rate control valve 710 is interposed in the piping Li5. On the other hand, an open / close valve 750 is interposed in the hydraulic pressure discharge line Lo.
Here, the hydraulic pump 500, the oil tank 600, and the on-off valve 750 are the same as those shown in FIG. That is, the hydraulic pressure supply source of the frame 30 and the casing 20 is common.
A symbol B3 in FIG. 12 indicates a (second) branch point of the hydraulic pressure supply line.

In the sleeve 38 configured as described above, the casing 20 is closed by closing the on-off valve 750 and adjusting the opening of the flow rate adjusting valve 710, operating the hydraulic pump 500, and supplying compressed oil to the sealed space. The movement of the second rod 23 in the left-right direction and the rotational direction can be restricted. In other words, the movable shaft 300 can be temporarily fixed at an arbitrary position, and the connection work with the counterpart rotation shaft to be connected can be facilitated.
On the other hand, in order to loosen the restraint of the second rod 23 in the left-right direction and the rotational direction, the hydraulic pressure on the sleeve side is lowered by stopping the hydraulic pump 500 and opening the on-off valve 750, and the restraint by the hydraulic pressure of the movable shaft 300 is released. .
In order to simplify the entire apparatus, it is possible to omit the hydraulic circuit and the sealed space as described above (use of a sleeve without a depression).

  A stepped through hole 32c through which a positioning pin is inserted and penetrated is formed at a position corresponding to the positioning hole 29 formed in the vertical member 21 of the casing 20 in one of the left and right vertical members 32. Further upward, the spring S3 and the bias of the spring S3 are positioned at positions corresponding to the through holes 21c for storing the spring S3 for returning the original position of the left-right rotation formed in the vertical member 21 of the casing 20. A through hole 32b is formed for feeding a means (not shown) for adjusting the angle to the through hole 21c.

A lift mechanism for lifting the second rod 23 of the casing 20 is provided below the left and right caps 36.
In the storage hole 36a of the bearing case 230C of the cap 36, a bearing 230 that supports the second rod 23 in an auxiliary manner is stored via the bearing case 230C. A block 39 is formed on the lower surface of the cap 36. In the block 39, two spring accommodating holes 39a are formed on each of the left and right sides. A female screw is formed in the spring housing hole 39a, and after the above-described spring S6 is housed in the housing hole 39a, the adjustment bolt B60 screwed into the female screw is screwed to push up the bearing case 230C. The second rod 23 of the casing 20 can be easily moved left and right and also smoothly rotated.
On the contrary, by loosening the adjustment bolt B60, the second rod 23 is fixed at an arbitrary horizontal position or at an arbitrary angle. Therefore, by changing the height of the adjustment spring S6 as described above, it is possible to easily perform the work during assembly.

  According to the alignment mechanism 1 having the above-described configuration, even when the bearing 10 is moved downward by the return springs S1 and S2 and the return mechanism (adjustment nut N1), it can be easily returned to the original position. Further, the presence of the return spring S1 is biased in a direction against the mass of the bearing 10 or the casing 20 of the alignment mechanism 1 and has an elastic repulsive force substantially equal to the mass. Does not require great force for assembly.

  By providing the return spring S3, the rotation angle of the bearing 10 can be returned to the original position even when the bearing 10 rotates around the vertical axis.

  By installing the return spring S4, the casing 20 can be returned to the original position even when the casing 20 moves left and right.

  When the return spring S5 is mounted, the bearing 10 can be returned to the original position when the bearing 10 moves in the front-rear direction, and rotation occurs around the second rod 23 of the casing 20, which is a horizontal axis. In addition, the bearing 10 can be returned to the original angle.

  Further, the adjustment spring S6 adjusts the biasing force to the second rod 23 by adjusting the lower end of the adjustment spring 6S up and down to facilitate the rotation of the second rod 23 and the sliding in the rod axis direction. On the other hand, the rotation of the second rod 23 and the sliding in the rod axis direction can be made easy and positioning can be performed at the time of assembly.

  Equipping the original position return springs S2, S3, S4, and S5 makes it easy to align during assembly.

  The transmission plate 9 is attached in the vicinity of the tip of the first extension rotary shaft 100 connected to the movable shaft 300 and connected to the engine-side flywheel 82, and is connected to the tip of the axis of the first extension rotary shaft 100. Fixes the pin P. The pin P is inserted into a bearing 83 provided at the center of the flywheel 82 on the engine side and is pivotally supported so that it can be easily aligned with the output shaft 81 of the engine.

  It should be noted that the illustrated embodiment is merely an example, and is not a description to limit the technical scope of the present invention.

The side view which shows the structure of the whole measuring apparatus which concerns on embodiment of this invention. Sectional drawing which showed the AA cross section of FIG. 1 typically. The detail drawing which expanded and showed the B section of FIG. FIG. 3 is an enlarged detailed view of a portion C in FIG. 2. The side view of the alignment mechanism which concerns on embodiment of this invention. FIG. 6 is a front view corresponding to FIG. 5. The side view which showed the detailed structure of the bearing which concerns on embodiment of this invention. The front view corresponding to FIG. The side view which showed the detailed structure of the casing which concerns on embodiment of this invention. The front view corresponding to FIG. The schematic diagram which shows the detailed structure of the frame which concerns on embodiment of this invention. The front view corresponding to FIG. The figure which showed the state in which only the deflection angle produced in the joint part in the motoring test method which has the three shafts connected. The figure which showed the state in which the deflection angle and eccentricity produced simultaneously in the joint part in the motoring test method which has three connected shafts. FIG. 14 is a ZZ arrow view in FIG. 13.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 ... Center alignment mechanism 2 ... Inverter motor 5 ... Torque detector 6 ... Flywheel 7 ... Flywheel bearing 8 ... Engine 9 ... Transmission plate 10 ... Bearing 15 ... first rod 16 ... bias adjustment rod 20 ... casing 23 ... second rod 24 ... sleeves 25, 26 ... cap 27 ... bias adjustment Rod 30 ... Frame 35 ... Bearing portion 36 ... Cap 38 ... Sleeve 81 ... Output shaft 82 ... Flywheel 100 ... First rotary shaft / first extension Rotating shaft 200 ... second rotating shaft / second extending rotating shaft 300 ... third rotating shaft / movable shaft S1-S5 ... original position returning spring S6 ... adjusting spring J1. ..Free coupling / free joint

Claims (7)

  In a rotary shaft connecting mechanism that connects first and second rotary shafts whose center lines are not necessarily on the same straight line, a universal coupling configured to have zero backlash, a universal coupling connected to the universal coupling, and a first coupling A third rotating shaft connected to the first rotating shaft, and an alignment mechanism that supports the third rotating shaft, the aligning mechanism including the first and second rotating shafts. It is configured so that it can be accurately positioned with respect to any one of the rotating shafts, and the third rotating shaft can be rotated but can be fixed so as not to swing. A rotating shaft connecting mechanism.   The alignment mechanism includes a pair of first rods that are supported on a third rotation shaft and extend in the vertical direction or the horizontal direction perpendicular to the axis of the third rotation shaft and are arranged coaxially. A bearing having the first rod of the bearing supported by the first bearing hole and extending orthogonally to the pair of rods in a direction orthogonal to the axis of the third rotating shaft and arranged coaxially A casing having a pair of second rods, and a frame that pivotally supports the second rod of the casing by a second bearing hole, wherein the first rod is the first rod. 2. The rotation according to claim 1, wherein the second rod is configured to be slidable and rotatable in the bearing hole, and the second rod is configured to be slidable and rotatable in the second bearing hole. Axis connection mechanism.   The first bearing hole and the second bearing hole have a fixing member for fixing the first and / or second rod, and the first and / or second rod is fixed by the fixing member. Accordingly, the position of the bearing in the casing and the position of the casing in the frame are determined, and when the fixing member is in the unlocked state, the first and / or second rods are the first and / or Or the inside of a 2nd shaft hole is comprised so that a slide and rotation are possible, The rotating shaft connection mechanism of Claim 2 characterized by the above-mentioned.   Of the first and second rods, a lower end portion of the rod extending in the downward direction of the bearing and a bottom portion of the bearing hole extending in the downward direction of the bearing among the first and second bearing holes are formed. The elastic member which is urged | biased in the direction which opposes the mass of the bearing or casing of the said alignment mechanism between the reference surfaces to perform and has an elastic repulsion force substantially equal to the said mass is interposed. The rotating shaft connecting mechanism according to any one of 3.   The rotary shaft connection according to any one of claims 2 to 4, wherein an elastic member that urges the rod in the axial direction of the third rotary shaft is interposed at end portions of the first and second rods. mechanism.   The first rotating shaft is a rotating shaft connected to the engine output shaft system or the engine output shaft system, the second rotating shaft is a shaft connected to the output shaft of the electric motor, and the third rotation 6. The shaft according to claim 1, wherein the shaft is directly connected to the engine output shaft system via the transmission plate or to the engine output shaft system via the transmission plate via the first rotating shaft. The rotating shaft connection mechanism of the term.   The transmission plate is fixed to the third rotating shaft side, and a pin is fixed on the same axis as the third rotating shaft, and the pin is supported by a bearing provided on the output side of the engine. The rotating shaft connecting mechanism according to claim 6, wherein the rotating shaft connecting mechanism is configured to be aligned with the output shaft of the engine.

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