JP6586973B2 - Viscous rotor rear absorber that shifts at an angle. - Google Patents

Description

Detailed Description of the Invention

The present invention relates to a rotary type variable speed roller type damping device.

Absorbers that absorb shocks are used to open and close rear trunks, bonnets, and doors of houses. In particular, for doors, a large shift is required within a small range of 90 degrees such as delayed action, back check, and latching. A rotary absorber built in the hinge axis is desirable, but there is no rational means. Currently, a method of damping the door with a linkage by controlling it in the middle of the stroke of the cylindrical cylinder and piston that is attached to the door is popular. However, it is expensive, complicated, and requires a place because it is attached separately from the hinge.

JP-A-2014-224597 roller clutch, FIG. Patent

  No oil leakage due to accuracy error, temperature, thermal strain, foreign matter biting, etc. of current hydraulic parts described in the background art, no complicated linkage etc., simple and inexpensive, constant regardless of load size The purpose of this is to be able to change the speed of the door freely and to adjust easily to changes in temperature.

  In reciprocating opening and closing, a normal turning range is a swing of 180 degrees or less, and a kind of one-way clutch function is required that attenuates when closing and reduces resistance when opening. It takes about 5 to 8 seconds to open and close at the door, and wheelchair users should slowly close for 5 to 6 seconds after opening up to 120 degrees and then pass through, and then there will be no problem from around 60 degrees It turns to speed and closes quietly without sound at the end. The damping speed is adjusted according to the weight and length of the door and the opening area. The incidental function requires a function that locks for a moment under a rapid load of a back check that prevents personal injury when closing suddenly due to a strong wind. A similar suppression function is required on the opening side.

  The present invention uses the principle of the roller clutch of Prior Art Patent Document 1. The characteristic curves to be obtained are the lower parts a, b and c in FIG. In FIG. 1, the vertical axis represents speed, the horizontal axis represents the operation time, and the operation curve until the door 68 is closed is indicated by a dotted line. Reference numeral 70 is a first speed range, 72 is a second speed range, 71 is a third speed range, and finally 73 is a latching operation, and shows a normally required pattern. FIG. 2 shows a hinge 12 such as a door according to a typical embodiment, a hinge 12 fixed to the stationary side, a hinge 13 fixed to the turning side (movable side), and central portions 15 and 38 of the movable and fixed sides. A cross section is shown in FIGS. FIG. 3 shows an embodiment in which only one roller type damping device of the present invention is used, and a plurality of members having the same structure are used in combination as shown in FIGS.

  A roller 5a in which the outer diameter surface of the shaft 1 in FIG. 3 and the inner diameter surface of the outer ring 3 are partly conical surfaces of a single-leaf rotating hyperboloid and are skewed with respect to the center line of the shaft between the conical surfaces. Are held by a cage 4 so that a plurality of rolls can be rolled. In this configuration, when torque is applied between the shaft and the outer ring, the skewed roller 5a bites between the conical surfaces by the wedge action, and the shaft 1 and the outer ring 3 are elastically displaced relative to each other in the rotational direction and the axial direction. As a result, a high-pressure confined oil film is formed on the contact surface of the roller.

  The static torque capacity in this configuration is 14 permanent rollers with a roller diameter of Φ2mm and a length of 17mm, the average diameter of the shaft is Φ14mm, the outer diameter of the outer ring is Φ35mm, and the contact has a permanent strain (Brinell impression) with a depth of 0.0001mm. The remaining torque is 10 kg-m. In addition, the wedge angle is 1.8 degrees at the initial stage and changes to about 3 degrees due to elasticity. When the lubricating oil is applied, an oil film having a thickness of 0.3 microns is confined in the contact and flows out from the surroundings over time, and at that time, a squeeze fluid film is formed around the contact. In the viscous torque experiment, the surface pressure is 1 GPa with repeated 2 kg-m load, and the fatigue life of SUJ-2 high cleanliness steel is permanent if a lubricant is obtained.

  In doors, etc., the roller rotates freely by overturning when opening and overrunning. In normal rotation, when molybdenum disulfide or fluororesin is added to the lubricating oil, creep (hereinafter referred to as viscous creep rotation) rotates at the above-mentioned constant speed regardless of the magnitude of the load torque. When an abrupt torque is applied, the oil film solidifies and shifts for a moment at high pressure and locks (backstop), and immediately returns to the original creep rotation. The principle is presumed that oil molecules are interposed between the layered crystal grains of molybdenum disulfide to be added and the displacement is displaced at high pressure. When the displacement is displaced, the roller rolls slightly and entrains new oil, so that it rotates continuously in a viscous manner.

In this state, if the tension of the surface pressure of the roller evenly distributed on the circumference is loosened, the creep speed increases. The means is shown in FIG. 9 of the above-mentioned Patent Document 1 (current applicant), schematic diagram 3 of the principle, and partial diagram (b ).

  The condition that determines the speed of creep rotation in this configuration is a displacement due to plastic deformation of the high-pressure confined oil film at the contact point of the roller, and therefore depends on the viscosity of the oil, the diameter of the roller to revolve, and the diameter of the roller. Further, the lubricant used has a high traction coefficient and low temperature dependence, and requires extreme pressure additives such as organic molybdenum disulfide and fluorine.

The means according to claim 1, wherein the outer diameter of the shaft and the inner diameter surface of the outer ring are made into a single-leaf rotating hyperboloid, and a plurality of rollers that are skewed with respect to the center line of the shaft can be rolled between the shaft and the outer ring by the cage means An uneven cam profile member corresponding to the rotational angle of the relative rotation between the shaft and the outer ring and a pin member slidably contacting the shaft member are provided between the shaft and the outer ring, and are shifted at the relative rotational angle. Get a viscous rotary rear absorber.

A unit composed of the shaft, outer ring, and roller is arranged in a double row in place of the speed change means of claim 1 on the movable side and the fixed side, respectively, between the movable outer ring and the shaft, or on the movable side. A stopper member 6a for turning on and off the relative rotation of the shaft and the outer ring at every angle of relative rotation between the movable side and the fixed side is interposed between the outer side and the shaft of the movable side and the shaft. A viscous rotor rear absorber that shifts at a fixed relative rotation angle is obtained.

With a simple component configuration of shaft, outer ring, roller, cage, and grease, a huge torque viscous resistance can be obtained, so if it is built in a hinge, it is a hydraulic cylinder and linkage that is externally mounted on a conventional door, a seal, and a seal The complicated system which consists of etc. becomes unnecessary.

..Attenuation characteristic curve ..Opening / closing device assembly exterior schematic view ・ ・ (A) Single row roller type damping device assembly appearance schematic view (b) Correlation graph of stress distribution and speed due to couple load .. 1 of the double row embodiment of claim 2, embodiment of deceleration by key block (A) .. 2 of the double row embodiment of claim 2, schematic view of the embodiment of the shift hook (b). .. 3 of the embodiment of claim 2, the appearance of the transmission ratchet and the fitting and desorption action explanatory diagram Curve graph of the speed transmission embodiment (A) .. Combined embodiment of claims 1 and 2 (b) .. Characteristic curve at the time of combination (A), (b), (c), (d), (e), (f), and various combinations of the double-row roller damping device and the skew direction of the roller are added. (G) Example cross section ..Example of Patent Document 1

The embodiment of claim 1 will be described in detail with reference to FIG. 3, wherein the fractional view (b) shows the reverse thrust force giving the speed of viscous rotation and the horizontal axis on the vertical axis. The upper part of the curve is a schematic diagram in which the viscosity resistance of the solidified oil film increases and decreases and the speed changes according to the degree of reverse thrust. In FIG. 3, (a), when the shaft 1 is turned in the direction of the arrow 51, the outer ring 3 is engaged with the urging force of the disc spring 56 and the skew angle of the roller by the traction of the oil film. , And relative rotation with viscous resistance. At the same time, relative displacement in the axial direction is generated by the elastic displacement of the hertz of the contact in proportion to the torque. At this time, the annular eccentric cam 8 rotated by the pin member 7 fixed to the outer diameter of the shaft by press-fitting is slidably contacted with the profile 11 on the side surface of the outer ring 3, and the side surface of the outer ring 3 is pushed, so that the outer ring And the shaft is separated in the axial direction. Then, as shown in the partial diagram (b), the roller rolls while slackening the tightening force of the roller, so that it propagates to the entire area and the surface pressure decreases and becomes faster. The speed of the operating angle range changes according to the shape of the mountain of the profile. When the cam passes through the mountain and reaches the valley, it returns to the original speed.

  The speed of the door is gradually changed by combining the peak 11 of the profile, the cam 8, the inertia of the door, the biasing spring, and the viscous resistance. After a person passes, the cam goes over the mountain of the profile and gets back to its original speed. Providing a mountain just before closing speeds up for latching. The variation in the viscosity of the oil due to the temperature is dealt with by adjusting the amount of eccentricity of the eccentric cam 8 in FIG. During reverse thrust loading, the backstop function (backcheck) is lost, but there is no problem because the angle range is narrow.

In this application, a semi-permanent lifetime is essential, and in order to ensure this, it is essential to maintain a stable lubricant. Therefore, a cup-shaped resin piston 81 also serving as a check valve is screwed onto the hinge shaft screw 82, and pumping is performed by opening and closing the door to circulate the built-in grease so that the hole 80 and the shaft center through hole can be circulated. (Not shown) Supply. Therefore, the circulation pump is provided for all the following embodiments.

Embodiment of the first means of claim 2,
The outer diameter of the shaft according to claim 1 and the inner diameter surface of the outer ring are made into a single-leaf rotating hyperboloid, and a plurality of rollers skewed with respect to the center line of the shaft are interposed between the shaft and the outer ring by a cage means so as to be able to roll. Viscous rotor rear absorbers are arranged on the movable side and the fixed side, respectively, as shown in FIG. 4, and provided with U-shaped notch grooves facing each other on the side surfaces of the outer and outer rings 3a and 3b on the movable side and the fixed side. , A rectangular key block 6 projecting to the outer diameter side is provided. The block 6, a groove 3a of the U-shaped, 3b, the engagement Then slow operating angular 61s, a high-speed operating angular 61f, but determined by the widths of the grooves.

In this state, the fixed side is set to double the speed of the viscosity of the oil agent described in [013], the diameter at which the roller revolves, and the diameter of the roller relative to the speed of viscosity of the movable roller. 4, the width of the cut-out groove on the movable side and the operating range 61 s of the key block 6 are converted to, for example, an angle of 40 degrees, and the fixed side 61 f is also set to 70 degrees. When the door is opened and closed by 110 degrees, first, the movable side and the fixed side are started at the same time, and the operating speed of the door starts to close at 61s on the movable side and the total speed on the fixed side. When the fast speed fixed side turns 70 degrees, the block 6 collides with the groove end and stops, and the remaining 40 degrees closes only on the slow speed movable side .

  Use the difference in friction resistance during overrunning when opening the door, because the slow side operates immediately before it closes securely. When the frictional resistance of the overrunning on the movable side is increased, the slow side with the lower friction first overruns, so the operating range 61s is secured first, and the movable side with the larger friction follows later. In this way, even if the door is opened 20 degrees, only the slow side with low friction opens with overrunning and closes gently. As a means for imparting frictional resistance, a metal G-shaped circlip with little change with time is used between the shaft and the outer ring, and sliding contact friction is obtained by a pressing force in the radial direction. As shown in FIG. 1, (a), the characteristic curve of the viscosity speed of this system is closed at the speed of the sum of both the movable side and the fixed side at first, and from the middle to only one slow speed on the movable side. Switching and decelerating can eliminate the sound of closing doors suitable for quiet environments.

When embedding the member of the said structure in the floor of a door , it is set as the parallel arrangement | positioning of 74 of the division | segmentation figure (g) of FIG. 8 with respect to the serial arrangement of the axial direction of FIG. Therefore, an intermediate member 74 is provided between the shaft and the outer ring, and the direction of the skew is reversed on the inner and outer races so that the thin roller 5a is arranged on the low speed side and the thick roller 5b is arranged on the high speed side . U-shaped notch grooves 61s and 61f are provided on the side surfaces of the intermediate member 74 and the outer ring 3b, respectively . The intermediate member 74 is provided with the key block 6a, and the shaft 1 is also provided with the same 6b. The shaft and the intermediate member are first stopped at each angle, and then the intermediate member and the outer ring are stopped from rotating relative to each other in order . The torque flow is indicated by a dotted line and an arrow 70.72 in the figure. Even if the torque is the same between the inside and outside of the intermediate member, the amount of elastic displacement (distance) in the axial direction is different. For this reason, the thickness of the outer ring 3b and the number of rollers are increased or decreased to align the amount of elastic displacement in the axial direction. The thrust load is a bearing system in which the shaft center is received by a steel ball. FIG. 8 shows examples (a), (b), (c), (d), (e), and (f) of the arrangement of the shaft (inner ring) and outer ring, the roller skews 5a and 5b, and the torque flow thereof by arrows .

FIG. 5 of the second embodiment of claim 2 will be described in detail. Grooves 61 and 62 shaped respectively to the side of the instead 5 minutes view slow movable speeds shown in (a) and fast velocity fixed side of the case is not required a step of shifting much aforementioned key block outer ring co, the S-shaped hook 65 to be engaged, Ru and provided. During the high speed, the claw 65b of the S-shaped hook rotates in sliding contact with the groove bottom 62 of the stationary outer ring 3b, and when the step reaches the groove bottom, the claw 65b rides on the step and the direction of the hook changes. Instead, the hook claw 65a, which has stopped the movable side, comes out of the groove and switches to a slower speed on the movable side. The torque flow is indicated by broken lines 70 and 72 in FIG .

The position of the switching angle between the torque paths 70 and 72 is set by the width of the groove 61 of the outer ring that reverses the S-shaped hook of the developed view (b) of FIG .

The action of the S-shaped hook is shown in part (b) of FIG. The number (1) given to (b) is an S-shaped hook 65 that rotates around the central pin 66 of the shaft 1 and shows the relative positional relationship between the shaft and the outer ring when the door starts to close from the fully open position. One protrusion 65a of the two protrusions on the outer periphery of the outer periphery fits into the notch groove 61 on the side surface of the movable outer ring. When the movable outer ring rotates from here to the closing side, the other protrusion 65b of the hook 60 comes into contact with the protrusion 62 on the side surface of the outer ring on the fixed side, so that the hook 60 rotates counterclockwise and rotates to the opposite protrusion 65a. Is forcibly removed from the groove of the movable outer ring. As a result, the movable outer ring and the shaft 1 become free and the slow side starts to rotate. Immediately after that, if the positions of the end stopper 64a of the shaft 1 and the groove end 64b of the fixed outer ring are brought into contact with each other, the positions of the groove end 64b of the fixed outer ring and the groove of the movable outer ring are removed. The shaft 1 on the fast side and the stationary outer ring 3b immediately lock and stop.

This state is indicated by (c) in the drawing, and from the position of number (3), the movable outer ring 3a is rotated by the slow roller 5a, and the door is closed gently. When the door is opened from the position (5) in the partial diagram (c), the numbers (6) to (7) are obtained. Even if the door is further opened from the position (7), the outer ring 3a on the movable side is moved integrally with the hooks 65a and the protrusions 63 of the shaft fitted to the groove ends 67 and 68. Since the movable outer ring is in the state of (3) in the partial drawing (b) even if it is inverted from there to the closing side, the hook tip 65a is in the groove 68. The high-speed shaft 1 and the fixed-side outer ring 3b are locked, so that only the low-speed side rotates and closes gently. By making the frictional resistance smaller than the fast side during overrunning, the slow stroke is always secured in a certain range first, and the slow stroke is operated only immediately before the last closing. In FIG. 4, the S-shaped movable hook 63 is urged counterclockwise by a spring (not shown) in FIG. In the embodiment of FIG. 4, in order to speed up the fixed side, the roller diameter on the fixed side of the speed setting requirement described above is large and the revolution diameter of the roller rolling is reduced.

  In the third embodiment, the first embodiment, and the second embodiment of claim 2, once decelerating, the speed cannot be increased. For this reason, a concavo-convex profile is provided on the side surface of the claw and the ratchet and the movable outer ring shown in FIG. 6 between the aforementioned movable outer ring, the shaft, and the fixed outer ring. The torque path is changed to broken lines 70 and 72 in FIG. The slide key tip is slidably contacted with the concave / convex profile on the side of the outer ring, the key is reciprocated in the axial direction with the concave / convex, the ratchet is fitted and disengaged, and the rotation of one side is interrupted, so that the speed of double row addition and the speed of one piece Change gears.

  6, the slide key 48, which is prevented from rotating by engaging with the outer peripheral key groove of the fixed outer ring 3b on the right side of FIG. 6, is urged by the spring 55 in the left direction. The inclined surface 49 a is engaged with the ratchet teeth 50 on the side surface of the outer peripheral rib in the center of the shaft 1. Then, since the outer ring 3b and the shaft 1 are locked by the key, the relative rotation of the right shaft and the outer ring 3a is stopped. As a result, the rotational speed is only the speed on the left side of the movable side. When the movable outer ring rotates further in the closing direction from the position, the protrusion crest 53a is pushed back to the right by the outer side 49b of the tip of the key, and then the right outer ring and the shaft begin to freely rotate out of the ratchet. It becomes the speed of the sum of both. This characteristic is shown in FIG. 1C, that is, according to the means, the speed can be changed to an arbitrary speed.

  FIG. 7A is an embodiment in which the third means of claim 1 and claim 2 are combined, and the upper half of the circumference of the shaft 1 is the speed increase by the couple of claim 1 and the bottom. The half can obtain further fine control by fitting and disengaging the ratchet according to claim 2. In this embodiment, since the shaft is not positioned in the rotational direction, the position of the corrugation between the shaft and the outer ring shifts when the door is repeatedly opened and closed. Therefore, when the outer ring is opened, the pin 8 protruding to the outer diameter shown in the right sectional view of FIG. 6B and the restoring hook 47 protruding in the axial direction from the side surface of the outer ring, the outer ring is attached to the shaft. Reset by means of accompanying.

Embodiment of claim 3 In this configuration, the relative displacement in the axial direction of the shaft and the outer ring is about 2 mm, and the outer diameter of the outer ring 3 is slidably slidably contacted by the spline 10 to be a sliding contact surface. The film is coated with a low friction coefficient fluororesin that also serves as a lubricant and rust.
Further, as shown in FIG. 3, by utilizing the relative rotation of the shaft and the outer ring, the piston 81 is moved in the axial direction by the spiral groove 82 provided between the two and the non-rotating pin 83, and the oil agent is moved by the piston. The oil passage grease hole 80 is circulated by being fed from the communication hole 84 to a roller rolling part (not shown).
The shaft, outer ring, and roller are hardened and tempered to a bearing steel hardness of HRC60 or higher, and the rolling surface of the roller is ground to a roundness of 0.002 mm or less. The rolling roller 4 is made of iron or resin. Hold in the vessel 5.

FIG. 3 shows a transmission system using the first embodiment and reverse thrust.
Embodiment 2 FIG. 4 shows means for decelerating with a key block in a double row.
FIG. 5 shows a means for switching the speed at the central S-shaped hook in the third embodiment.
Embodiment 4 FIG. 6 shows an embodiment in which a ratchet at the center of the shaft is fitted and removed at an angle to change speed.
Example 5, which is a combination of Example 2 and 2 to 4, Example 6 shown in FIG. 7, Example of arrangement of shaft and outer ring is shown in FIG. 8, (a) to (g),
Only (g) is shown for the key block, others are omitted.
Example 7, Example in which the damper is provided in both forward and reverse directions. (Not shown).
Example 8, to protect the device from damage due to accidental over-torque, escape by slipping the excess torque of a resin bush having tighten b between the outer diameter and the hinge inner diameter of the outer ring. (Not shown)
[Embodiment 9] FIG. 4 shows an embodiment of a pump that circulates grease by opening and closing swinging motion.

The present invention relates to a rotary buffer absorber. A highly versatile mechanical element applicable to all devices that attenuate and mitigate impact in the rotational direction, and a rotary type absorber mechanism that transforms and attenuates the cylindrical reciprocating rocking mechanism into the rotational direction.

1 ·· Shaft 3a, 3b · · Outer ring 4 · · Cage 5, 5a, 5b · · Roller 6 · · Key block 6a · · Swing angle stopper 8 · · Cam 12, 13 · · Hinge 46 · · · Restoring pin ··········································································· Slide key 49a ··· Sliding contact surface with ratchet teeth at the tip of the key 49b・ ・ Ratchet teeth 55 ・ ・ Spring 60 ・ ・ Hook 61 ・ ・ Notch groove on fixed outer ring 61s, 61f ・ ・ Operating range of viscous rotation (key groove)
63 .. Shaft protrusion stoppers 64a and 64b. End stoppers 65a and 65b... Hook protrusion tips 66... Pin 74... Intermediate member 75.

Claims (3)

  Viscous rotor rear absorber with a cage means between the shaft and outer ring so that the outer diameter of the shaft and the inner diameter surface of the outer ring are single-lobed hyperboloids and a plurality of rollers that are skewed with respect to the center line of the shaft can roll. And a means for changing speed by providing an uneven profile member in which a plurality of high and low peaks corresponding to the angle of relative rotation between the shaft and the outer ring, and a cam member slidably contacting the profile member between the shaft and the outer ring. Viscous rotary rear absorber. An uneven profile member in which a plurality of high and low peaks corresponding to a rotation angle of relative rotation between the shaft and the outer ring according to claim 1 and a cam member slidably contacting the profile member are provided between the shaft and the outer ring. Instead of the means for shifting the speed, a viscous rotor rear vortexer formed by interposing a roller between the shaft and the outer ring is disposed on the movable side and the fixed side, respectively, and the space between the outer ring and the shaft on the movable side is arranged. Alternatively, a stopper for stopping the relative rotation is provided between the movable outer ring and the shaft and the fixed outer ring and the shaft, and the stopper for stopping the relative rotation is turned on / off according to the angle of the relative rotation. A variable-speed viscous rotor rear absorber.   3. The viscous rotor rear absorber according to claim 1 or 2, wherein the oil retained in the space between the shaft and the outer ring is circulated by moving the piston member in the axial direction by the action of relative rotation of the shaft and the outer ring. A viscous rotor rear absorber having the piston member for circulating the oil agent.

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