CN102146978B - Rotating damper - Google Patents

Abstract

The invention provides a rotating damper which can automatically adjust a braking force corresponding to a load change and does not have a structure not easy to be damaged. Control gaps (11, 12) are disposed between a cylindrical housing (1) and a rotor (2) with a blade (6) and enable a pressure chamber at a high-pressure side to be communicated with a pressure chamber at a low-pressure side. A thrust chamber (13) is provided for introducing pressure of the high-pressure side. A structure is formed and is characterized in that the rotor (2) moves corresponding to the pressure difference between a pressure chamber side compression face of a flange (9) integratedly disposed on the rotor (2) and a thrust chamber side compression face, thereby the sizes of the control gaps (11, 12) can be controlled.

Description

Rotation damper

Technical field

The present invention relates to adjust automatically corresponding to payload the rotation damper of torque.

Background technique

In the past, the rotation damper that makes it low to rotate about the object that rotates is applied braking force had a kind of known dawn of rotation damper that can adjust its braking force corresponding to load automatically.

This rotation damper that can adjust braking force corresponding to load automatically possesses such advantage: for example is installed to toilet seat or toilet cover and uses, and when replacings such as toilet seat back weight has change, also still can be to close with the same low degree before changing.

This rotation damper is appeared at patent documentation 1 (TOHKEMY 2009-186016 communique).It divides the fluid chamber that is formed in the shell with being formed at the blade on the running shaft and being formed at next door on the shell, obtains braking force by the resistance of the fluid that flows through the fluid passage that forms on blade or the next door.On above-mentioned blade or next door, the flow control division that utilizes leaf spring to adjust above-mentioned fluid passage flow is set.This flow control division is regulated flow corresponding to load, and the braking force of loading when big is also big, and load hour braking force is also little.

Above-mentioned rotation damper in the past is because flow control portion is arranged on the next door of the blade of running shaft or shell, so the component parts of this flow control portion is minimum.There is such problem in this minimum parts: not only rapid wear, and flow control scope is little, can't enlarge the adjustment range of braking force.

Summary of the invention

Purpose of the present invention just is that providing a kind of can adjust braking force automatically and possess the rotation damper that is difficult for damage structure corresponding to load variations.

Purpose of the present invention is achieved as follows.

First invention is a kind of rotation damper, arranges in the shell of tubular when sense of rotation has load and does the time spent with respect to the counterrotating rotor of above-mentioned shell; Form the pressure chamber with blade portion and next door in above-mentioned shell, this blade portion forms towards the inwall of above-mentioned shell in the periphery of this rotor, and this next door is outstanding to above-mentioned rotor from the interior Zhou Dynasty of above-mentioned shell; In the process of above-mentioned rotor rotation, this pressure chamber is that the boundary is divided into high pressure side and low voltage side with above-mentioned blade portion; The feature of above-mentioned rotation damper is: axial distolateral in above-mentioned epitrochanterian above-mentioned blade portion forms the flange body that contacts with the inwall of above-mentioned shell; Between the end in this flange body and above-mentioned next door and between the face faced of the axial the other end of above-mentioned blade portion and this other end, the pair of control gap that formation is communicated with the high pressure side of above-mentioned pressure chamber and low voltage side, but also arrange and the thrust chamber of facing mutually with a face above-mentioned blade portion opposite side above-mentioned flange body; On above-mentioned flange body, arrange pressure chamber's side compression face that the on high-tension side pressure of above-mentioned pressure chamber works with the relative thrust chamber side compression face of above-mentioned pressure chamber side compression face.

And the area of above-mentioned thrust chamber side compression face is established greatlyyer than the area of above-mentioned pressure chamber side compression face, and possesses the elastic member that above-mentioned rotor is applied elastic force on the direction that above-mentioned control gap is widened; Form a structure, the pressure that the high pressure side of above-mentioned pressure chamber is produced acts on formed pressure chamber, both sides side compression face and the thrust chamber side compression face of above-mentioned flange body, the elastic force that makes above-mentioned rotor resist above-mentioned elastic member corresponding to the difference in areas of two compression faces moves vertically, thereby makes above-mentioned pair of control gap smaller; The on high-tension side pressure that forms the pressure chamber that produces by the torque that acts on above-mentioned rotor is controlled the structure of the size of above-mentioned control gap.

Further, can also be by the i.e. first concavo-convex cooperation that cooperates of the protuberance on being formed at above-mentioned epitrochanterian recess or protuberance and being formed at above-mentioned shell or recess, form and make above-mentioned rotor rotation and along above-mentioned axially movable first guide mechanism.

Second invention is based upon on the above-mentioned first invention basis, it is characterized in that: on above-mentioned rotor, the running shaft that is made of the parts that set up with above-mentioned rotor is set; Form a structure, it is mobile vertically with respect to above-mentioned shell to limit this running shaft, and allows above-mentioned running shaft to rotate with above-mentioned rotor one.

Further, allow above-mentioned running shaft with the structure of above-mentioned rotor one rotation, can be by being formed at recess on the above-mentioned running shaft or protuberance and being formed at cooperating of above-mentioned epitrochanterian protuberance or recess, i.e. the second concavo-convex cooperation realizes.

Also have, above-mentioned elastic member can insert above-mentioned recess and be between above-mentioned recess and the raised part.

The 3rd invention is based upon on the above-mentioned first invention basis, it is characterized in that: be wholely set running shaft at above-mentioned rotor, and form the structure that above-mentioned rotor and above-mentioned running shaft move along above-mentioned axial one relative to above-mentioned shell.

The 4th invention is a kind of rotation damper, arranges in the shell of tubular when sense of rotation has load and makes the time spent rotor rotated; Form the pressure chamber with blade portion and next door in above-mentioned shell, this blade portion forms towards the inwall of above-mentioned shell in the periphery of this rotor, and this next door is outstanding to above-mentioned rotor from the interior Zhou Dynasty of above-mentioned shell; In the process of above-mentioned rotor rotation, this pressure chamber is that the boundary is divided into high pressure side and low voltage side with above-mentioned blade portion; The feature of above-mentioned rotation damper is: with an end face of above-mentioned rotor the moving member that can move vertically is set relatively; At above-mentioned moving member and above-mentioned rotor relative position vertically, form the control gap that the high pressure side that makes above-mentioned pressure chamber and low voltage side are communicated with, but also in an opposite side with above-mentioned control gap thrust chamber is set across above-mentioned moving member; On the side of the control gap side of above-mentioned moving member, pressure chamber's side compression face that the on high-tension side pressure of above-mentioned pressure chamber works is set, and the side of the thrust chamber side of above-mentioned moving member is made as thrust chamber side compression face.

And the area of above-mentioned thrust chamber side compression face is established greatlyyer than the area of above-mentioned pressure chamber side compression face; Between above-mentioned rotor and above-mentioned moving member, be arranged on the elastic member that direction that above-mentioned control gap widens applies elastic force again; Form a structure, the pressure that the high pressure side of above-mentioned pressure chamber is produced acts on above-mentioned pressure chamber side compression face and above-mentioned thrust chamber side compression face, the elastic force that makes above-mentioned moving member resist above-mentioned elastic member corresponding to the difference in areas of two compression faces moves vertically, thereby above-mentioned control gap is diminished; The on high-tension side pressure that forms the pressure chamber that produces by the torque that acts on above-mentioned rotor is controlled the structure of the size of above-mentioned control gap.

In addition, on above-mentioned the 4th invention basis, can also be wholely set running shaft at above-mentioned rotor, and form the relative above-mentioned shell with above-mentioned running shaft of the above-mentioned rotor of restriction along the above-mentioned structure that moves axially.Can also arrange like this: above-mentioned moving member has the flange part that above-mentioned control gap and above-mentioned thrust chamber are demarcated, and two faces of this flange part constitute above-mentioned pressure chamber side compression face and above-mentioned thrust chamber side compression face respectively.Further, can also allow above-mentioned elastic member be between above-mentioned rotor and the above-mentioned flange part.

Also have, on above-mentioned the 4th invention basis, when possessing above-mentioned flange part, can arrange like this: the central vertical in above-mentioned flange part arranges a portion, above-mentioned running shaft passes this one, makes above-mentioned moving member along above-mentioned axially movable second guide mechanism thereby form.In addition, also can arrange like this this moment: the central vertical in above-mentioned flange part arranges a portion, by as the above-mentioned tube portion of protuberance or recess be formed at above-mentioned shell on recess or protuberance cooperate i.e. the 3rd concavo-convex cooperation, form and make above-mentioned moving member along above-mentioned axially movable the 3rd guide mechanism.Further, when being formed with the 3rd guide mechanism, can be by the above-mentioned tube portion and i.e. the 4th concavo-convex cooperation that cooperates that is formed at above-mentioned epitrochanterian recess or protuberance as protuberance or recess, form and make above-mentioned rotor rotation and make above-mentioned moving member along above-mentioned axially movable the 4th guide mechanism.

Also have, on above-mentioned the 4th invention basis, when adopting the above-mentioned third and fourth concavo-convex cooperation, can allow above-mentioned elastic member insert above-mentioned recess and be between above-mentioned recess and the raised part.

In addition, on above-mentioned first to fourth invention basis, can arrange like this: above-mentioned blade portion comprises the blade on the periphery that is formed at above-mentioned rotor and the front end that is enclosed within this blade and directly and the spacer that contacts in interior week of above-mentioned shell; Only at above-mentioned rotor when not producing the direction rotation of braking force, the blade portion path that formation makes the high pressure side of above-mentioned pressure chamber be communicated with low voltage side between the front end of above-mentioned blade and above-mentioned spacer.At this moment, can also be between the front end of above-mentioned blade and above-mentioned spacer and the sense of rotation of above-mentioned rotor form the gap, and form grooving at above-mentioned blade and above-mentioned spacer respectively, form above-mentioned blade portion path by above-mentioned gap and above-mentioned grooving.

Further, on above-mentioned first to fourth invention basis, on above-mentioned flange body or above-mentioned flange part, can also form the through hole (this through hole is in the position corresponding with above-mentioned high side pressure chamber) that above-mentioned pressure chamber and above-mentioned thrust chamber are communicated with.

The present invention has following effect.

According to the rotation damper of first to fourth invention, rotor or moving member can move and the size of adjustment control gap vertically corresponding to input torque.Therefore, can abandon in the past the sort of easy damage structure and accomplish and to adjust braking force corresponding to torque.

According to second invention, because rotor and running shaft are to set up parts, running shaft not opposite shell is mobile vertically, therefore can reduce the wearing and tearing of slip surface between running shaft and shell.

Also have, for the linkage structure between the other side's parts that connect with shell or running shaft, can consider to move axially, this makes linkage structure become simple.

In addition, when running shaft was integrally formed at the flange side, in order to ensure the thrust chamber side compression area of flange body, running shaft can not be done too slightly.And according to second invention, because rotor and running shaft set up, the size of flange body is not restricted, and running shaft can be done very slightly.So tackle high torque (HT) easily.

According to the 3rd invention, because rotor and running shaft are integrated, compare with setting up occasion, can reduce number of components.

Also have, because the linkage structure of rotor and running shaft becomes unnecessary, structure is simplified, so accomplish miniaturization on the whole easily.

According to the 4th invention, owing to be to move the size of adjusting control gap vertically by moving member, opposite shell is mobile vertically for running shaft.Therefore, become simple with the linkage structure between the other side's parts of shell or running shaft connection.

Also have, even if the axial dimension precision of rotor is relatively poor, also can adjust control gap by the movement of moving member, so the axial dimension precision of rotor or shell needn't be established very accurately, thereby make the manufacturing of component become light.

Description of drawings

Fig. 1 is the axial sectional view of first mode of execution.

Fig. 2 is the stereogram of a part of parts of first mode of execution.

Fig. 3 (a) is the sectional view along III-III line among Fig. 1.

Fig. 3 (b) is the sectional view that shows the state when rotor rotates along the y direction.

Fig. 4 is the low torque view on the section of III-III line in Fig. 1.

Fig. 5 is the high torque (HT) view on the section of III-III line in Fig. 1.

Fig. 6 is the sectional view along VI-VI line among Fig. 1 that shows the high torque (HT) state.

Fig. 7 is the sectional view along VII-VII line among Fig. 1.

Fig. 8 is the sectional view of second mode of execution.

Fig. 9 is the sectional view along IX-IX line among Fig. 8.

Figure 10 is the sectional view along X-X line among Fig. 8.

Figure 11 is the sectional view of the 3rd mode of execution.

Figure 12 (a) is the partial sectional view of moving member in the 3rd mode of execution.

Figure 12 (b) is the plan view of moving member in the 3rd mode of execution.

Figure 13 is the sectional view along XIII-XIII line among Figure 11.

Figure 14 is the sectional view along XIV-XIV line among Figure 11.

Figure 15 is the sectional view of the 4th mode of execution.

Figure 16 is the sectional view along XVI-XVI line among Figure 15.

Figure 17 is the sectional view along XVII-XVII line among Figure 15.

Figure 18 is the sectional view of the 5th mode of execution.

Figure 19 is the sectional view along XIX-XIX line among Figure 18.

Figure 20 is the sectional view of the 6th mode of execution.

Figure 21 is the sectional view along XXI-XXI line among Figure 20.

Figure 22 is the sectional view along XXII-XXII line among Figure 20.

Among each figure, 1 expression shell, 2 is rotor, and 3 is running shaft, and 4 is helical spring, 6 is blade, and 7 is the next door, and 8 is spacer, and 9 is flange body, 9a, 9b are face, and 9a ' is pressure chamber's side compression face, and 9b ' is thrust chamber side compression face, and 10 is through hole, 11,12 is control gap, and 13 is thrust chamber, and 16 is moving member, and 17 is flange part, 17b, 17c are face, and 19 is intercommunicating pore, and 20 is control gap, and 21 is thrust chamber, 22 is moving member, and 23 is flange part, and 23a, 23b are face, and 25 is intercommunicating pore.

Embodiment

Fig. 1～Fig. 7 illustrates first mode of execution of the present invention.

Fig. 1 is the sectional view that contains axis, and Fig. 3～Fig. 7 is the sectional view with the axis quadrature.In addition, Fig. 1 also is the sectional view along a-a line among Fig. 3, Fig. 4 and Fig. 5 also be with the same section of Fig. 3 on sectional view.

Also have, between Fig. 6 and Fig. 3 and Fig. 7, because profile direction is opposite, so the sense of rotation on the section is opposite.Among the figure, rotor rotates when identical, and its sense of rotation adopts same arrow to represent.

Also have, Fig. 1 also is the original state schematic representation of torque when not acting on running shaft 3 and rotor 2.

The rotation damper of this first mode of execution is a kind of like this rotation damper: rotor 2 can be assembled in the relative rotation in the shell 1 of tubular, import viscous fluid between shell 1 and rotor 2, the flow resistance of the viscous fluid during by the 1 relative rotation of rotor 2 and shell obtains braking force.

For example above-mentioned shell 1 is fixed on toilet body, and when rotor 2 being connected on the running shaft of toilet seat, then can applies braking force to the toilet seat rotation, in case toilet seat falls with sudden force.

Direction of insertion front end at above-mentioned rotor 2 is formed with recess 2a, and is formed with the protuberance 1a that is inserted in this recess 2a at shell 1.So, in above-mentioned recess 2a, insert in the raised part 1a (constituting the so-called first concavo-convex cooperation), also between this protuberance 1a front end and recess 2a bottom surface, assemble helical spring 4, to apply the power on the direction that widens between the two that makes, namely the back will illustrate makes power on the direction that control gap 11,12 widens.

But rotor 2 is set as the elastic force that can resist helical spring 4 and moves vertically.

Also have, as Fig. 1, Fig. 2 and shown in Figure 7, be formed with protuberance 2b in the direction of insertion rear end of rotor 2,2b connects running shaft 3 by this protuberance.

Above-mentioned running shaft 3 has large-diameter portion 3a in rotor 2 one sides, is formed with the recess 3c that inserts raised part 2b at its end face 3b.Embed this recess 3c (constituting the so-called second concavo-convex cooperation) by the protuberance 2b with above-mentioned rotor 2, rotor 2 and running shaft 3 are coupled together, thereby just the rotating force of running shaft 3 can be passed to rotor 2.

Further, by above-mentioned large-diameter portion 3b is clamped with the step 1b and the lid 5 that are formed on the shell 1, running shaft 3 is rotatably supported under the state of vertically mobile restricted system.

Also have, be formed with a pair of blade 6,6 in the periphery of rotor 2, and in shell 1, be formed with a counter septum 7,7 week.Further, the front end of above-mentioned blade 6 be with directly with shell 1 in all spacers 8 that is roughly " コ " font that contacts, this spacer 8 is integrated with blade 6 front ends and moves, blade 6 contacts with shell 1 by above-mentioned spacer 8.

In addition, in this first mode of execution, constitute blade of the present invention portion by above-mentioned blade 6 and spacer 8.

But maintaining such size relationship between the fore-end of above-mentioned blade 6 and the spacer 8: on the sense of rotation of rotor 2, be formed with the gap between the two.

Also have, on above-mentioned blade 6 and spacer 8, be formed with grooving 6a, 8a respectively.These be for when above-mentioned rotor 2 along Fig. 3 (a), can form access p during arrow y direction rotation shown in (b) and establish (referring to Fig. 3 (b)), its details aftermentioned.

In addition, also all be such in following arbitrary mode of execution: above-mentioned access p is communicated with when above-mentioned rotor 2 rotates along arrow y direction.But only provided rotor 2 along the rotation of arrow y direction in Fig. 3 (b) and the state that above-mentioned access p is communicated with, other mode of executions also can be with reference to this figure.

And, by above-mentioned blade 6,6 and next door 7,7 form 4 A of pressure chamber, B, C, D in the enclosure.

The capacity of these pressure chambers is along with rotor 2 changes with the relative rotation of shell 1, and in the present embodiment, the above-mentioned A of pressure chamber is the same with the C variation, and the B of pressure chamber changes the same with D.

Particularly, when rotor 2 rotated along arrow x direction, the A of pressure chamber and C became the low-pressure lateral pressure chamber of expansion, and the B of pressure chamber and D become the high side pressure chamber that dwindles.

At this moment, shown in Fig. 3 (a), the pressure of high side pressure chamber B and D acts on above-mentioned spacer 8, and spacer 8 is pressed and above-mentioned grooving 6a is blocked to blade 6.For this reason, blade 6,6 and spacer 8,8 between, obstructed via the access p of above-mentioned grooving 6a and grooving 8a.

Otherwise when rotor 2 rotated along arrow y direction, the A of pressure chamber and C became the high side pressure chamber that dwindles, and the B of pressure chamber and D then become the low-pressure lateral pressure chamber of expansion.

At this moment, the pressure that is derived from high side pressure chamber A and C acts on spacer 8, and spacer 8 leaves the grooving 6a of blade 6.So, be formed at grooving 8a on the spacer 8 and the grooving 6a of blade 6 and meet, form access p.For this reason, shown in arrow among Fig. 3 (b), fluid flows to low-pressure lateral pressure chamber B and D from high side pressure chamber A and C by above-mentioned access p.

Further, the part periphery beyond the blade 6,6 of rotor 2 is formed with groove 2c (referring to Fig. 2 and Fig. 3).As shown in Figure 4, when above-mentioned next door 7 top ends and this groove 2c met, this groove 2c played the effect that makes the access that the A of pressure chamber and D, the B of pressure chamber be connected with C.

Also have, be formed with flange body 9 at above-mentioned rotor 2, flange body 9 and blade 6 axial one distolateral be that the end face of running shaft 3 sides links to each other, and have and the contacted diameter of shell 1 inwall.

And, be formed with the through hole 10,10 that the face 9b from the face 9a of blade 6 sides to opposition side connects at this flange body 9.Shown in Fig. 2,6,7, these through holes 10,10 are located near the blade 6,6, and are in the corresponding position, high side pressure chamber, pressure chamber of a side of dwindling when arrow x direction is rotated with rotor 2 opposite shell 1.

Also have, can be mobile vertically in shell 1 with rotor 2 with the blade 6 that above-mentioned spacer 8 is integrated.And, under state shown in Figure 1, above-mentioned blade 6 in the axial direction with next door 7 dislocation of shell 1.

In addition, in the both end sides of blade 6 with the formed pressure chamber of 7 axial overlap parts, next door, form control gap 11,12 respectively.That is, forming control gap 11 between the next door 7 of face 9a of above-mentioned flange body 9 and shell, is then to form control gap 12 between the direction of insertion front end of rotor 2 and the bottom surface that its opposing side is shell 1 at the axial the other end of blade of the present invention portion.These control gaps 11,12 make by between blade 6 and the pressure chamber that next door 7 is divided and are communicated with.

In addition, state shown in Figure 1 is that pack into the above-mentioned rotor 2 of shell 1 is pressed against state on the running shaft 3 because of the elastic force of helical spring 4.Under this state, between the above-mentioned end face 3b of another face 9b of flange body 9 and running shaft 3, be formed with thrust chamber 13.

This thrust chamber 13 or above-mentioned control gap 11,12 can be guaranteed by the axial dimension that suitably designs each several part.

In addition, symbol 14 expression O type circles among the figure, 15 expression packing rings.

Below, this rotation damper is once regulated torque corresponding to the load that acts on above-mentioned running shaft 3 principle is described.

The state of the Fig. 1 that acts on above-mentioned running shaft 3 when never loading has rotating force to act on running shaft 3, and during rotor 2 rotations, the capacity of each A of pressure chamber, B, C, D changes.

For example, when rotor 2 was rotated along arrow x direction, the B of pressure chamber, D became the high side pressure chamber that dwindles, and the C of pressure chamber, A then become the low-pressure lateral pressure chamber of expansion.

At this moment, as mentioned above, blade 6,6 and spacer 8,8 between do not form access p.

So, as shown in Figure 4, during the groove 2c of next door 7 and rotor 2 meets, owing to not only flow via above-mentioned control gap 11,12 to the low-pressure lateral pressure chamber A of expansion, the fluid that C moves from the high side pressure chamber D, the B that dwindle, but also flow via above-mentioned groove 2c, so the rotation of rotor 2 is not subjected to the effect of braking force, keep brisk rotation.

From Fig. 4, rotor 2 further leaves groove 2c along arrow x direction rotation, next door 7 and when becoming situation shown in Figure 5, is blocked via the mobile of above-mentioned groove 2c, and fluid is only via above-mentioned control gap 11,12 and flow.Therefore, corresponding with these control gaps 11,12 flow path area resistance is applied in the rotation of rotor 2 as rotation brake power.

At this moment, on a face 9a of above-mentioned flange body 9 with above-mentioned high side pressure chamber B, part that D is corresponding, form the side compression face 9a ' of pressure chamber that high side pressure works.This compression face 9a ' is the part that the high side pressure on a face 9a of flange body 9 works, and is with the part shown in the site among Fig. 6.

Also have, in the thrust chamber 13 of another face 9b that faces above-mentioned flange body 9, import the pressure of the B of pressure chamber, D by the through hole 10 that forms on the flange body 9.That is, the pressure of high side pressure chamber B, D is imported in the thrust chamber 13, acts on the thrust chamber side compression face 9b ' shown in the site among Fig. 7.

As mentioned above, two compression face 9a ', 9b ' at flange body 9 have high side pressure to work, but, also can obviously find out from Fig. 6 and Fig. 7, owing to be formed with blade 6, spacer 8 and next door 7 in pressure chamber's side, the area of thrust chamber side compression face 9b ' wants specific pressure chamber side compression face 9a ' big.Therefore, there is the pressure of pressing to control gap 11 sides from thrust chamber 13 to work at flange body 9.

But, owing to have the elastic force of the above-mentioned helical spring 4 that rotor 2 is pressed to thrust chamber 13 thrusters to work at rotor 2, so rotor 2 maintains the position that pressure that the difference in areas of above-mentioned thrust chamber side compression face 9b ' and the side compression face 9a ' of pressure chamber produces and elastic force balance each other.

That is, the high side pressure that two compression face 9a ', 9b ' of above-mentioned flange body 9 go up effect is more high, to control gap 11,12 directions that narrow down than original state shown in Figure 1 are moved, strengthens the braking force to rotation.

In addition, the torque that acts on rotor is more high, and it is more high that above-mentioned high side pressure also can become.For example, the parts such as toilet seat that are installed on the running shaft 3 are more heavy, and it is more high that high side pressure also becomes thereupon, thereby produce the thrust make on the direction that control gap 11,12 diminishes.Therefore, rotor 2 can move vertically corresponding to acting on the torque on the running shaft 3, adjusts the braking force to rotation automatically.

In addition, above-mentioned control gap 11,12 is along with rotor 2 movement in the axial direction, synchronously becomes big or diminishes.So as long as the axial extent of two control gaps is made as equal, just can accomplish to make simultaneously two control gaps is zero, raising braking force.But two control gaps also can wait greatly,

In addition, in this first mode of execution, above-mentioned control gap 11,12 flow path area are done forr a short time than the flow path area of the flow path area of above-mentioned access p and above-mentioned groove 2c.And be arranged to: when the connection of above-mentioned access p or groove 2c is blocked, fluid is only by above-mentioned control gap 11,12 and when flowing, even above-mentioned control gap 11,12 is in original state and also has braking force to a certain degree to be applied in, rotational speed is slowed down.

On the other hand, when rotor 2 rotated along arrow y direction among the figure, the A of pressure chamber, C became the high side pressure chamber that dwindles, and the D of pressure chamber, B then become the low-pressure lateral pressure chamber of expansion.

At this moment, shown in Fig. 3 (b), blade 6,6 with spacer 8,8 between above-mentioned access p be communicated with.Therefore, fluid almost is that non-resistance ground flows from the A of pressure chamber, C to the B of pressure chamber, D by this access p.

And compression face 9a ' shown in Figure 6 does not constitute the compression face that high side pressure works.In addition, because the through hole 10,10 that forms at above-mentioned flange body 9 is corresponding to low-pressure lateral pressure chamber D, B, thereby above-mentioned thrust chamber 13 does not import high side pressure.Therefore, rotor 2 can not occur and move because of the pressure of thrust chamber 13, control gap 11,12 is diminished.

That is, when guaranteeing that above-mentioned control gap 11,12 sizes are certain, above-mentioned access p is communicated with, and viscous fluid flows via above-mentioned access p and control gap 11,12, thus the not restricted dynamic action of the rotation of rotor 2, brisk rotation.

In addition, at rotor 2 when the arrow y direction rotation, if when meet with the groove 2c that is formed at above-mentioned rotor 2 in above-mentioned next door 7 as shown in Figure 4, because fluid also flows through this groove 2c, so that flow resistance can become is littler.Even if but this groove 2c is blocked, fluid also can be by above-mentioned access p and control gap 11,12 and almost be that non-resistance ground flows.

As mentioned above, the rotation damper of this first mode of execution, when rotor 2 rotates along arrow y direction, almost be the effect of brakeless power and brisk rotation, and when when the rotation of arrow x direction, then can adjust braking force automatically corresponding to acting on the torque on the running shaft, its rotational speed is also almost constant even if above-mentioned torque changes.

In this first mode of execution, though make that number of components is corresponding and increase because rotor 2 and running shaft 3 constitute separately, can bring following benefit.

If when above-mentioned running shaft 3 is made as one with rotor 2, because running shaft 3 will move vertically, just need the axially movable structure of permission be set with the joint that is installed on the miscellaneous part on the running shaft 3.And if as present embodiment, the occasion that running shaft 3 does not move vertically just becomes simply with the linkage structure of miscellaneous part, nor running shaft 3 can occur because moving axially problem easy to wear.

In addition, when running shaft 3 and rotor 2 are made as one, make the thrust chamber side compression face 9b of the flange body 9 of rotor 2, bigger, just can't do the diameter of running shaft 3 too big.And if as this first mode of execution, constitute the occasion of rotor 2 and running shaft 3 separately, and then do not have this restriction, can adopt large diameter running shaft 3.Therefore, can improve the intensity of running shaft 3, tackle higher commentaries on classics distance.

Fig. 8～second mode of execution shown in Figure 10 be a kind of on rotor 2 example of integrally formed running shaft 3.

Here, though also different with above-mentioned first mode of execution on the supported this point movably in the axial direction in running shaft 3 opposite shell 1, still use identical title and symbol for function with the same structural element of first mode of execution.

In addition, be located at the next door 7 of blade 6,6, spacer 8, flange body 9 and shell 1 on the rotor 2,7 structure, all with above-mentioned first mode of execution the same (referring to Fig. 2 and Fig. 9).

The rotation damper of this second mode of execution also misplaces above-mentioned blade 6,6 under original state shown in Figure 8 and assembles with next door 7,7 axial position.

And, between face 9a of above-mentioned flange body 9 and next door 7, be provided with control gap 11, and between the bottom surface that end face and its opposing side of the same flange body 9 opposite sides on the rotor 2 is shell 1, be formed with control gap 12.

Also have, at running shaft 3 large-diameter portion 3d is set, compress this large-diameter portion 3d with covering 5, cooperate the elastic force of helical spring 4 to keep the axial position of rotor 2 again.

The rotation damper of this second mode of execution also is like this: in case have rotating force act on running shaft 3, when rotor 2 rotates, the A of pressure chamber, the B that is divided by blade 6 and spacer 8 and next door 7, the capacity of C, D will change, viscous fluid will move.

So, when above-mentioned rotor 2 along as Fig. 9 and arrow x direction shown in Figure 10 when rotating, the B of pressure chamber and D dwindle and become the high pressure side, the A of pressure chamber and C then enlarge and become low voltage side.

So, when the A of pressure chamber, B, C, D become in high pressure side and the low voltage side, high pressure side and low voltage side are communicated with by above-mentioned control gap 11 and 12.Therefore, fluid flows from high side to low side by this a pair of control gap 11 and 12.

In addition, in this second mode of execution, also the position corresponding to above-mentioned high side pressure chamber B, D is formed with through hole 10,10 on above-mentioned flange body 9.Therefore, high side pressure is directed to thrust chamber 13, and above-mentioned high side pressure had both acted on the side compression face 9a ' of pressure chamber of flange body 9, also acted on thrust chamber side compression face 9b '.

So, when the pressure difference that acts on flange body 9 both sides can be contended with the elastic force of above-mentioned helical spring 4, flange body 9 will be towards above-mentioned control gap 11,12 directions that diminish are moved.

Also be like this at this second mode of execution: corresponding to the level of torque that acts on the running shaft 3, rotor 2 is mobile vertically, adjustment control gap 11,12 size.Its result can access and the corresponding braking force of torque.

In addition, when running shaft 3 rotates along arrow y direction among Fig. 9 and Figure 10, also the same with above-mentioned first mode of execution, blade 6,6 with spacer 8,8 between the access p shown in Fig. 3 (b) be communicated with, viscous fluid almost is that non-resistance ground flows from the A of pressure chamber, C to the B of pressure chamber, D by this access p.

And, because above-mentioned through hole 10 does not correspond to the high side pressure chamber, so thrust chamber 13 does not import high side pressure.Therefore, rotor 2 can not occur moves and control gap 11,12 is diminished.

Thereby, when rotating along above-mentioned arrow y direction, the not restricted dynamic action of the rotation of rotor 2, brisk rotation.

In addition, in this second mode of execution, because rotor 2 is integrally formed with running shaft 3, so compare with the rotation damper of above-mentioned first mode of execution, can accomplish to reduce number of components.Yet, because running shaft 3 is mobile vertically, just need with parts that toilet seat etc. and running shaft 3 are connected between the axially movable linkage structure of permission is set.

Figure 11～the 3rd mode of execution and above-mentioned first mode of execution difference shown in Figure 14 is: do not establish flange body at rotor 2, but possess moving member 16.

In this 3rd mode of execution, still use identical title and symbol for function with the same structural element of first mode of execution.

In addition, in this 3rd mode of execution, be located at the next door 7,7 structure of blade 6,6, spacer 8 and shell 1 on the rotor 2 also all with above-mentioned first mode of execution the same (referring to Fig. 2 and Figure 14), its explanation of Therefore, omited.

Also have, running shaft 3 has large-diameter portion 3a, and by this large-diameter portion 3a is clamped with the step 1b and the lid 5 that are formed on the shell 1, it is mobile vertically to limit running shaft 3.And, in this 3rd mode of execution, because rotor 2 is integrally formed with running shaft 3, so moving axially also of rotor 2 is limited.

Also have the forward end on the direction of inserting to shell 1 of above-mentioned rotor 2, assembling moving member 16.

Above-mentioned moving member 16 is parts of shape shown in Figure 12 (a) and (b), comprising: have the flange part 17 of the diameter of the periphery of making contact shell 1 inwall, at the minor diameter part 18a of the forward end of outstanding tube portion 18 of the central authorities of this flange part 17 and this one 18.

The above-mentioned tube of protuberance 1a insertion portion 18 (the constituting so-called the 3rd concavo-convex cooperations) that the bottom surface central authorities of shell 1 are set, and again tube portion 18 is inserted the recess 2a (constituting so-called the 4th concavo-convex cooperation) that is formed on the rotor 2, and make these a few shells 1, rotor 2 and moving member 16 keep coaxial.

In addition, also the minor diameter part 18a of above-mentioned tube portion 18 is inserted the center of helical spring 4.

Also have, on above-mentioned flange part 17, form next door 7 set on shell 1 inwall, 7 a pair of grooving 17a, the 17a that embed wherein, simultaneously, also form intercommunicating pore 19 continuously with this grooving 17a.This intercommunicating pore 19 constitutes an access that face 17b side is communicated with another face 17c side that makes flange part 17.

And, next door 7 is embedded above-mentioned grooving 17a and moving member 16 is assembled on the shell 1.Therefore, the rotation of above-mentioned moving member 16 is restricted, and can only be along the next door 7 moves axially.

Also have, as shown in figure 13, in the flange part 17 of moving member 16, above-mentioned intercommunicating pore 19 becomes the opening on above-mentioned next door 7,7 next doors.The position of this intercommunicating pore 19 is in the corresponding part in high side pressure chamber of dwindling along arrow x direction when rotation capacity among Figure 14 with above-mentioned rotor 2.

Also have, with regard to the rotation damper of this 3rd mode of execution, the elastic force of helical spring 4 works in the direction that the distance that makes between moving member 16 and the rotor 2 widens, and under original state shown in Figure 11, maintains moving member 16 near the state of shell 1 bottom surface.

At this moment, between the end face of face 17b of the flange part 17 on the moving member 16 and blade 6, form control gap 20, and form thrust chamber 21 in another face 17c side.

Rotation damper with basis the 3rd mode of execution of said structure, when rotating along arrow x direction among Figure 14, become the corresponding intercommunicating pore 19 of the on high-tension side B of pressure chamber, D owing to being formed with in above-mentioned flange part 17 with dwindling, therefore on high-tension side pressure is imported into above-mentioned thrust chamber 21, and acting on thrust chamber side compression face is another face 17c of flange part.

And be control gap 20 sides in a face 17b side of flange part 17, have only the part corresponding with high side pressure chamber B, D just to constitute pressure chamber's side compression face that high side pressure works in the middle of above-mentioned the 17b.Therefore, by acting on the pressure of flange part 17 both sides, flange part 17 obtains to make the thrust on the direction that control gap 20 diminishes.

Thereby, the same with above-mentioned other mode of executions when above-mentioned high side pressure is high, moving member 16 can contend with helical spring 4 elastic force and move, can adjust control gap 20 corresponding to the torque that acts on the running shaft 3.

That is, this 3rd mode of execution also is like this: corresponding to the level of torque that acts on running shaft 3, adjust the size of control gap 20, can access the braking force corresponding with torque.

Also have, running shaft 3 is along arrow y direction when rotation among Figure 14, and is also the same with above-mentioned first mode of execution, blade 6,6 and spacer 8,8 between, access p shown in Fig. 3 (b) is communicated with, and viscous fluid almost is that non-resistance ground flows from the A of pressure chamber, C to the B of pressure chamber, D by this access p.

And, because the position of above-mentioned intercommunicating pore 19 is not corresponding with the high side pressure chamber, so thrust chamber 21 does not import high side pressure.Therefore, moving member 16 also can not occur moves and control gap 20 is diminished.

Therefore, when rotating along above-mentioned arrow y direction, the not restricted dynamic action of the rotation of rotor 2, brisk rotation.

Figure 15～the 4th mode of execution shown in Figure 17 is characterised in that: use the moving member 16 in above-mentioned the 3rd mode of execution of moving member 22 replacements, and this moving member 22 is located at running shaft 3 sides.

And, in this 4th mode of execution, be located at the next door 7,7 structure of blade 6,6, spacer 8 and shell 1 on the rotor 2 also all with first mode of execution the same (referring to Fig. 2 and Figure 16), its explanation of Therefore, omited.

But, form protuberance 2d at rotor 2 end faces, this protuberance 2d is inserted into the recess 1c that is formed at shell 1 bottom surface.And, allow running shaft 3 connect the lid 5 that is fixed on shell 1 opening, lean on the above-mentioned recess 1c of this lid 5 and shell 1 to come support rotor 2 and running shaft 3.

Moving member 22 in this 4th mode of execution comprises flange part 22 and tube portion 24; Be formed with intercommunicating pore 25,25 in flange part 23; This intercommunicating pore 25,25 when rotor 2 rotates along arrow x direction among Figure 16, is in the position corresponding with becoming the on high-tension side B of pressure chamber, D in the next door 7 of circumferencial direction near shell 1.

Also have, make running shaft 3 connect (thereby forming so-called second guide mechanism) from the center of above-mentioned flange part 23 and tube portion 24, and above-mentioned tube portion 24 is in cover 5 sides, thus guarantee cover 5 and flange part 23 between formation thrust chamber 21.

Further, be the boundary with above-mentioned flange part 23, with above-mentioned thrust chamber 21 opposite sides, between flange part 23 and rotor 2 assembling helical spring 4.This helical spring 4 produces the elastic force on the direction that makes two parts draw back the interval.

So, do not act at high side pressure under the original state shown in Figure 15 of above-mentioned thrust chamber 21, between flange part 23 and rotor 2, form control gap 20.The same with above-mentioned the 3rd mode of execution, this control gap 20 is to make gap by being communicated with between the blade 6 that is integrated with spacer 8 and the pressure chamber that the next door 7 of shell 1 is divided.

In addition, as Figure 15, shown in Figure 17, be formed with from 7 ends, above-mentioned next door continuous vertically guiding protuberance 1d, also be formed with the grooving 23c that matches with this protuberance 1d in flange part 23 simultaneously.These guiding protuberance 1d and grooving 23c are chimeric to limit moving member 22 rotations by making, and only allows that it moves axially.

The rotation damper of this 4th mode of execution also is like this: when along the torque of arrow x direction among Figure 16 during in running shaft 3, the face 23a that high side pressure acts on flange part 23 is namely on pressure chamber's side compression face corresponding with becoming the on high-tension side B of pressure chamber, D.

At this moment, above-mentioned high side pressure is imported into thrust chamber 21 from the locational intercommunicating pore 25 corresponding with the above-mentioned B of pressure chamber, D, and also acting on thrust chamber side compression face is another face 23b of flange part 23.

So above-mentioned moving member 22 is corresponding to the pressure on two compression faces that act on flange part 23 and above-mentioned elastic force, and is mobile vertically, adjust the size of control gap 20 according to its position.

This 4th mode of execution also is like this: corresponding to the level of torque that acts on the running shaft 3, moving member 22 is mobile vertically, adjusts the size of control gap 20.Its result can access the braking force corresponding with torque.

Also have, when rotor 2 rotated along arrow y direction among Figure 16, the access p shown in Fig. 3 (b) was communicated with, and the relative rotation of rotor 2 is not subjected to braking force, and this point is the same with above-mentioned the 3rd mode of execution.

Further, this moment is not because high side pressure imports thrust chamber 21, so moving member 22 is not mobile, and moving member 22 can not make above-mentioned control gap 20 diminish because of mobile, and this point is also the same with above-mentioned the 3rd mode of execution.

Figure 18 and the 5th mode of execution shown in Figure 19 are a kind of like this rotation dampers: flange body 9 is located on the rotor 2 and ends running shaft 3 opposite sides.Though it is different with above-mentioned first mode of execution to be located at the position of the flange body 9 on the rotor 2, still use identical title and symbol for function with the same structural element of first mode of execution.

In this 5th mode of execution, for the rotor 2 with flange body 9 is inserted in the shell 1 that is formed with next door 7, be at shell 1 underside side opening, in order to insert rotor 2, then with covering 26 closure of openings.

In shell 1, lid 26 protuberance 26a is inserted into the recess 2a (constituting the so-called first concavo-convex cooperation) on the end face of lid 26 sides that are formed at rotor 2, with support rotor 2; And the protuberance 3e of running shaft 3 is inserted into the recess 2e (constitute so-called the second concavo-convex cooperation) of running shaft 3 sides that are formed at rotor 2.

Also have, the same with first mode of execution, above-mentioned running shaft 3 and rotor 2 are by protuberance 2b and recess 3c couples together so that both can the one rotation.

And, be resisted against at the large-diameter portion 3a with running shaft 3 on the step 1b that is formed at shell 1 inwall and with lid 5 and clamp, move vertically with restriction running shaft 3, also running shaft 3 and rotor 2 are rotatably supported simultaneously.

Further, between above-mentioned running shaft 3 and recess 2e, insert helical spring 4, in order to the elastic force on the direction that rotor 2 and running shaft 3 are pulled away from is worked.

This 5th mode of execution also is like this: in blade 6 sides of above-mentioned flange body 9, form feasiblely by the control gap 11 that is communicated with between blade 6 and the pressure chamber that next door 7 is divided, then form thrust chamber 13 at its opposition side.In addition, also form another control gap 12 that the end face of blade 6 is faced in running shaft 3 sides of rotor 2.

Above-mentioned control gap 11, the 12nd is when the elastic force of rotor 2 opposing helical springs 4 and the gap that diminishes simultaneously when mobile.

Also have, also be formed with through hole 10,10 on the flange body 9 of present embodiment, this through hole 10,10 becomes the corresponding position of the on high-tension side B of pressure chamber, D when being in and being subjected to torque along arrow x direction shown in Figure 19 with rotor 2.

The rotation damper of this 5th mode of execution also is like this: during along the torque of arrow x direction shown in Figure 19 in running shaft 3, pressure chamber's side compression face of a face 9a of flange body 9 has high side pressure to work, and then has the high side pressure that imports thrust chambers 13 by above-mentioned through hole 10 to work at the thrust chamber side compression face of another face 9b side.

So the 5th mode of execution also is like this: above-mentioned rotor 2 is corresponding to the pressure on two compression faces that act on flange body 9 and above-mentioned elastic force and mobile vertically, adjusts control gap 11,12 size according to its position.

That is, this 5th mode of execution also is like this: corresponding to the level of torque that acts on the running shaft 3, rotor 2 is mobile vertically, adjustment control gap 11,12 size.Its result can access the braking force corresponding with torque.

Also have, when rotor 2 rotated along arrow y direction among Figure 19, the access p shown in Fig. 3 (b) was communicated with, and the relative rotation of rotor 2 is not subjected to braking force, and this point is the same with above-mentioned first mode of execution.

Further, this moment is not because high side pressure imports thrust chamber 13, so rotor 2 can not move and make above-mentioned control gap 11,12 diminish, and this point is also the same with above-mentioned first mode of execution.

Moreover, in this 5th mode of execution, because constituting separately with running shaft 3, brings with the same benefit of above-mentioned first mode of execution rotor 2.

Figure 20～the 6th mode of execution shown in Figure 22 is the example of integrally formed running shaft 3 on rotor 2.

And, except also can opposite shell with running shaft 3 support movably vertically this point different with above-mentioned the 5th mode of execution, other structures are all about the same with above-mentioned the 5th mode of execution.So still use identical title and symbol for function with the same structural element of above-mentioned the 5th mode of execution.

That is, this 6th mode of execution also is like this: make the flange body of being located on the rotor 29 be in a side opposite with running shaft 3, be formed with control gap 11 and thrust chamber 13 in its both sides.

In addition, also form another control gap 12 at rotor 2 with between covering 5.

Further, insert helical spring 4 at rotor 2 with between covering 5, in order to apply direction that both are pulled away from, namely make elastic force on above-mentioned control gap 11,12 directions that widen.

The rotation damper of this 6th mode of execution also is like this: during along the torque of arrow x direction shown in Figure 22 in running shaft 3, pressure chamber's side compression face of a face 9a of flange body 9 has high side pressure to work, and then has the high side pressure that imports thrust chambers 13 via above-mentioned through hole 10 to work at the thrust chamber side compression face of another face 9b side.

So the 6th mode of execution also is like this: above-mentioned rotor 2 is corresponding to the pressure on two compression faces that act on flange body 9 and above-mentioned elastic force and mobile vertically, adjusts control gap 11,12 size according to its position.

That is, this 6th mode of execution also is like this: corresponding to the level of torque that acts on the running shaft 3, rotor 2 is mobile vertically, adjustment control gap 11,12 size.Its result can access the braking force corresponding with torque.

Also have, when rotor 2 rotated along arrow y direction among Figure 22, the same with above-mentioned other mode of executions, the access p shown in Fig. 3 (b) was communicated with, and the relative rotation of rotor 2 is not subjected to braking force.

Further, this moment, rotor 2 can not move and make above-mentioned control gap 11,12 diminish, and was the same with above-mentioned the 5th mode of execution in this yet because high side pressure does not import thrust chamber 13.

In addition, in this 6th mode of execution, owing to be wholely set running shaft 3 at rotor 2, with adopting the 5th mode of execution that arranges separately to compare, has the advantage that can reduce number of components.

In above-mentioned the 5th, the 6th mode of execution, because flange body 9 is located at a side opposite with running shaft 3, so must insert running shaft 3 and rotor 2 respectively from the two ends of shell 1.So, need arrange at the two ends of shell 1 and cover 5 and 26.Though therefore number of components increases, but bring such benefit: by adjusting the axial fixed position of above-mentioned lid 26, the maximum value that can easily change control gap is the setting value of minimum braking force.

Also have, above-mentioned the first, the 2nd, the 5th and the 6th mode of execution all be do not establish moving member, by the rotor 2 mobile example of adjusting the control gap size vertically.In these mode of executions, can move axially relatively in order to make rotor 2 and next door 7, control gap is formed at the both sides, pressure chamber.So in these mode of executions, when rotor 2 moved vertically, two control gaps size separately was simultaneously with the changes in amplitude of this amount of movement.

Therefore, compare with the occasion of regulating a control gap by the movement of moving member, this mode that can adjust two control gaps simultaneously can also be brought the benefit that enlarges its adjustment range.

In addition, above-mentioned first to the 6th mode of execution all is being described under the following prerequisite: the relative rotation that the size of control gap is set to rotor 2 when above-mentioned access p is blocked with groove 2c can be subjected to the degree of braking force effect, even if it is also like this when reaching maximum.But the size of control gap also can be set to the degree that do not allow braking force work under original state.

So, when rotor 2 rotates along above-mentioned arrow y direction, as mentioned above, control gap is kept original state, therefore, as long as establish the control gap size of original state enough big, the above-mentioned access p of switch even if do not form corresponding to sense of rotation also can accomplish not the rotation of rotor 2 is applied braking force in the same old way.

Also have, even grooving 6a and the 8a that is formed on the set spacer 8 of above-mentioned blade 6 and its front end is not set, that is, blade 6 and spacer 8 is integrally formed and do not establish access p, and this structure also is feasible.And, there is not groove 2c good.If the access path in addition that these access p, groove 2c etc. are made of control gap is not set, even but above-mentioned control gap size is set to the degree that also has braking force to a certain degree to work under original state, then also can apply certain braking force during along above-mentioned arrow y direction rotation when rotor 2.

Utilizability on the industry is as follows.

The toilet seat of rotation damper etc. to be installed in order low rotating, even if change back weight change have been arranged, rotational speed is also constant, and therefore, the unprofessional person also can carry out the replacing of toilet seat etc.

Claims (20)

1. a rotation damper arranges in the shell of tubular when sense of rotation has load and does the time spent with respect to the counterrotating rotor of above-mentioned shell; Form the pressure chamber with blade portion and next door in above-mentioned shell, this blade portion forms towards the inwall of above-mentioned shell in the periphery of this rotor, and this next door is outstanding to above-mentioned rotor from the interior Zhou Dynasty of above-mentioned shell; In the process of above-mentioned rotor rotation, this pressure chamber is that the boundary is divided into high pressure side and low voltage side with above-mentioned blade portion; The feature of above-mentioned rotation damper is:

Axial one distolateral in above-mentioned epitrochanterian above-mentioned blade portion forms the flange body that contacts with the inwall of above-mentioned shell; Between the end in this flange body and above-mentioned next door and between the face faced of the axial the other end of above-mentioned blade portion and this other end, the pair of control gap that formation is communicated with the high pressure side of above-mentioned pressure chamber and low voltage side, but also arrange and the thrust chamber of facing mutually with a face above-mentioned blade portion opposite side above-mentioned flange body;

On above-mentioned flange body, arrange pressure chamber's side compression face that the on high-tension side pressure of above-mentioned pressure chamber works with the relative thrust chamber side compression face of above-mentioned pressure chamber side compression face; The area of above-mentioned thrust chamber side compression face is established greatlyyer than the area of above-mentioned pressure chamber side compression face, and possesses the elastic member that above-mentioned rotor is applied elastic force on the direction that above-mentioned control gap is widened; Form a structure, the pressure that the high pressure side of above-mentioned pressure chamber is produced acts on formed pressure chamber, both sides side compression face and the thrust chamber side compression face of above-mentioned flange body, the elastic force that makes above-mentioned rotor resist above-mentioned elastic member corresponding to the difference in areas of two compression faces moves vertically, thereby makes above-mentioned pair of control gap smaller; The on high-tension side pressure that forms the pressure chamber that produces by the torque that acts on above-mentioned rotor is controlled the structure of the size of above-mentioned control gap.

2. by the described rotation damper of claim 1, it is characterized in that:

By the i.e. first concavo-convex cooperation that cooperates of second protuberance on being formed at above-mentioned epitrochanterian first recess or first protuberance and being formed at above-mentioned shell or second recess, form and make above-mentioned rotor rotation and along above-mentioned axially movable first guide mechanism.

3. by the described rotation damper of claim 1, it is characterized in that:

The running shaft that is made of the parts that set up with above-mentioned rotor is set at above-mentioned rotor; Form a structure, limit this running shaft and move axially along above-mentioned with respect to above-mentioned shell, and allow above-mentioned running shaft to rotate with above-mentioned rotor one.

4. by the described rotation damper of claim 3, it is characterized in that:

Allowing above-mentioned running shaft with the structure of above-mentioned rotor one rotation, is by being formed at the 3rd recess on the above-mentioned running shaft or the 3rd protuberance and being formed at cooperating of above-mentioned epitrochanterian the 4th protuberance or the 4th recess, i.e. the second concavo-convex cooperation realizes.

5. by the described rotation damper of claim 2, it is characterized in that:

Above-mentioned elastic member insert above-mentioned first recess and be in above-mentioned first recess and above-mentioned second protuberance between, perhaps above-mentioned elastic member insert above-mentioned second recess and be in above-mentioned second recess and above-mentioned first protuberance between.

6. by the described rotation damper of claim 4, it is characterized in that:

Above-mentioned elastic member insert above-mentioned the 3rd recess and be in above-mentioned the 3rd recess and above-mentioned the 4th protuberance between, perhaps above-mentioned elastic member insert above-mentioned the 4th recess and be in above-mentioned the 4th recess and above-mentioned the 3rd protuberance between.

7. by the described rotation damper of claim 1, it is characterized in that:

Be wholely set running shaft at above-mentioned rotor, and form the structure that above-mentioned rotor and above-mentioned running shaft move along above-mentioned axial one relative to above-mentioned shell.

8. by the described rotation damper of claim 2, it is characterized in that:

Be wholely set running shaft at above-mentioned rotor, and form the structure that above-mentioned rotor and above-mentioned running shaft move along above-mentioned axial one relative to above-mentioned shell.

9. by the described rotation damper of claim 5, it is characterized in that:

Be wholely set running shaft at above-mentioned rotor, and form the structure that above-mentioned rotor and above-mentioned running shaft move along above-mentioned axial one relative to above-mentioned shell.

10. a rotation damper arranges in the shell of tubular when sense of rotation has load and makes the time spent rotor rotated; Form the pressure chamber with blade portion and next door in above-mentioned shell, this blade portion forms towards the inwall of above-mentioned shell in the periphery of this rotor, and this next door is outstanding to above-mentioned rotor from the interior Zhou Dynasty of above-mentioned shell; In the process of above-mentioned rotor rotation, this pressure chamber is that the boundary is divided into high pressure side and low voltage side with above-mentioned blade portion; The feature of above-mentioned rotation damper is:

With an end face of above-mentioned rotor the moving member that can move vertically is set relatively; At above-mentioned moving member and above-mentioned rotor relative position vertically, form the control gap that the high pressure side that makes above-mentioned pressure chamber and low voltage side are communicated with, but also in an opposite side with above-mentioned control gap thrust chamber is set across above-mentioned moving member;

On the side of the control gap side of above-mentioned moving member, pressure chamber's side compression face that the on high-tension side pressure of above-mentioned pressure chamber works is set, and the side of the thrust chamber side of above-mentioned moving member is made as thrust chamber side compression face, the area of above-mentioned thrust chamber side compression face is established greatlyyer than the area of above-mentioned pressure chamber side compression face; Between above-mentioned rotor and above-mentioned moving member, be arranged on the elastic member that direction that above-mentioned control gap widens applies elastic force again; Form a structure, the pressure that the high pressure side of above-mentioned pressure chamber is produced acts on above-mentioned pressure chamber side compression face and above-mentioned thrust chamber side compression face, the elastic force that makes above-mentioned moving member resist above-mentioned elastic member corresponding to the difference in areas of two compression faces moves vertically, thereby above-mentioned control gap is diminished; The on high-tension side pressure that forms the pressure chamber that produces by the torque that acts on above-mentioned rotor is controlled the structure of the size of above-mentioned control gap.

11. by the described rotation damper of claim 10, it is characterized in that:

Be wholely set running shaft at above-mentioned rotor, and form the relative above-mentioned shell with above-mentioned running shaft of the above-mentioned rotor of restriction along the above-mentioned structure that moves axially.

12. by the described rotation damper of claim 10, it is characterized in that:

Above-mentioned moving member has the flange part that above-mentioned control gap and above-mentioned thrust chamber are demarcated, and two faces of this flange part constitute above-mentioned pressure chamber side compression face and above-mentioned thrust chamber side compression face respectively.

13. by the described rotation damper of claim 12, it is characterized in that:

Above-mentioned elastic member is between above-mentioned rotor and the above-mentioned flange part.

14. by the described rotation damper of claim 12, it is characterized in that:

Central vertical in above-mentioned flange part arranges a portion, and above-mentioned running shaft passes this one, makes above-mentioned moving member along above-mentioned axially movable second guide mechanism thereby form.

15. by the described rotation damper of claim 12, it is characterized in that:

Central vertical in above-mentioned flange part arranges a portion, by as the above-mentioned tube portion of the 5th protuberance or the 5th recess be formed at above-mentioned shell on the 6th recess or the 6th protuberance cooperate i.e. the 3rd concavo-convex cooperation, form and make above-mentioned moving member along above-mentioned axially movable the 3rd guide mechanism.

16. by the described rotation damper of claim 15, it is characterized in that:

By the above-mentioned tube portion and i.e. the 4th concavo-convex cooperation that cooperates that is formed at above-mentioned epitrochanterian the 8th recess or the 8th protuberance as the 7th protuberance or the 7th recess, form and make above-mentioned rotor rotation and make above-mentioned moving member along above-mentioned axially movable the 4th guide mechanism.

17. by the described rotation damper of claim 16, it is characterized in that:

Above-mentioned elastic member insert above-mentioned the 7th recess and be in above-mentioned the 7th recess and above-mentioned the 8th protuberance between, perhaps above-mentioned elastic member insert above-mentioned the 8th recess and be in above-mentioned the 8th recess and above-mentioned the 7th protuberance between.

18. by each described rotation damper in the claim 1 to 17, it is characterized in that:

Above-mentioned blade portion comprises the blade on the periphery that is formed at above-mentioned rotor and the front end that is enclosed within this blade and directly and the spacer that contacts in interior week of above-mentioned shell; Only at above-mentioned rotor when not producing the direction rotation of braking force, the blade portion path that formation makes the high pressure side of above-mentioned pressure chamber be communicated with low voltage side between the front end of above-mentioned blade and above-mentioned spacer.

19. by the described rotation damper of claim 18, it is characterized in that:

Between the front end of above-mentioned blade and above-mentioned spacer and the sense of rotation of above-mentioned rotor form the gap, and form grooving at above-mentioned blade and above-mentioned spacer respectively, form above-mentioned blade portion path by above-mentioned gap and above-mentioned grooving.

20. by each described rotation damper in the claim 1～9,12～17,19, it is characterized in that:

Form the through hole that above-mentioned pressure chamber is communicated with above-mentioned thrust chamber at above-mentioned flange body or above-mentioned flange part, this through hole is in the position corresponding with above-mentioned on high-tension side pressure chamber.

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