JP3516106B2 - Valve seat surface structure - Google Patents
Valve seat surface structureInfo
- Publication number
- JP3516106B2 JP3516106B2 JP24242195A JP24242195A JP3516106B2 JP 3516106 B2 JP3516106 B2 JP 3516106B2 JP 24242195 A JP24242195 A JP 24242195A JP 24242195 A JP24242195 A JP 24242195A JP 3516106 B2 JP3516106 B2 JP 3516106B2
- Authority
- JP
- Japan
- Prior art keywords
- peripheral side
- inner peripheral
- outer peripheral
- piston
- valve seat
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
Landscapes
- Fluid-Damping Devices (AREA)
Description
【０００１】[0001]
【発明の属する技術分野】この発明は、油圧緩衝器のピ
ストン部を形成するピストン体におけるバルブシート面
構造の改良に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to improvement of a valve seat surface structure in a piston body forming a piston portion of a hydraulic shock absorber.
【０００２】[0002]
【従来の技術】一般に、多くの油圧緩衝器では、シリン
ダ内で摺動するピストン部を形成のピストン体は、その
端面たるバルブシート面に減衰バルブを隣接させている
が、例えば、図３に示す従来例としての油圧緩衝器のピ
ストン部Ｐを形成するピストン体１にあっても、その上
端面たる圧側のバルブシート面にリーフバルブからなる
圧側減衰バルブ２を隣接させている。2. Description of the Related Art Generally, in many hydraulic shock absorbers, a piston body forming a piston portion that slides in a cylinder has a damping valve adjacent to a valve seat surface which is an end surface thereof. Even in the piston body 1 forming the piston portion P of the hydraulic shock absorber as the conventional example shown, the compression side damping valve 2 formed of a leaf valve is adjacent to the pressure side valve seat surface which is the upper end surface thereof.
【０００３】そして、上記圧側のバルブシート面は、図
４にも示すように、圧側減衰バルブ２の内周端を定着さ
せる内周側固定部１１と、圧側減衰バルブ２の外周端を
離着座させる外周側シート部１２と、該外周側シート部
１２と内周側固定部１１との間に形成されて複数の圧側
ポート１３のそれぞれの下流側端を開口させる開口部１
４と、外周側シート部１２と内周側固定部１１との間に
形成されて各開口部１４を相互に連通する連通部１５
と、を有するように設定されている。On the pressure side valve seat surface, as shown in FIG. 4, the inner peripheral side fixing portion 11 for fixing the inner peripheral end of the pressure side damping valve 2 and the outer peripheral end of the pressure side damping valve 2 are seated separately. An outer peripheral side sheet portion 12 to be opened, and an opening 1 formed between the outer peripheral side sheet portion 12 and the inner peripheral side fixed portion 11 to open the downstream end of each of the plurality of pressure side ports 13.
4 and a communication portion 15 that is formed between the outer peripheral side seat portion 12 and the inner peripheral side fixed portion 11 and that communicates the openings 14 with each other.
And are set to have.
【０００４】因に、上記ピストン体１にあっては、図３
に示すように、圧側ポート１３の上流側端が下端面たる
伸側のバルブシート面に開口し、上端側の外周面とされ
る傾斜面に伸側ポート１６の上流側端が開口し、該伸側
ポート１６の下流側端が伸側のバルブシート面に離着座
可能に隣接された伸側減衰バルブ３に対向するとしてい
る。尚、図３は、図４中のＸーＸ線で示す縦断面図であ
る。Incidentally, in the piston body 1, as shown in FIG.
As shown in FIG. 3, the upstream side end of the compression side port 13 is opened to the expansion side valve seat surface which is the lower end surface, and the upstream side end of the expansion side port 16 is opened to the inclined surface which is the outer peripheral surface on the upper end side. It is assumed that the downstream side end of the expansion side port 16 faces the expansion side damping valve 3 which is adjacent to the expansion side valve seat surface so as to be able to be seated and separated. Incidentally, FIG. 3 is a longitudinal sectional view taken along line XX in FIG.
【０００５】それ故、この従来例とされる提案によれ
ば、ピストン部ＰがシリンダＣ内を下降する圧側作動時
には、圧側油室Ｌからの作動油が圧側ポート１３を通り
圧側減衰バルブ２とバルブシート面、正確には、外周側
シート部１２との間を介して伸側油室Ｕ内に流入し、そ
の際に、所定の圧側減衰力が発生されることになる。Therefore, according to this conventional proposal, when the piston portion P moves downward in the cylinder C, the hydraulic oil from the pressure side oil chamber L passes through the pressure side port 13 and the compression side damping valve 2. It flows into the expansion side oil chamber U via the valve seat surface, more precisely, the space between the outer peripheral side seat portion 12, and at that time, a predetermined compression side damping force is generated.
【０００６】[0006]
【発明が解決しようとする課題】しかしながら、上記の
提案にあっては、ピストン速度が低速域から中速域にあ
るときには、圧側減衰バルブ２に設定通りの減衰力の発
生を期待できるが、ピストン速度が中速域を過ぎて特に
高速域になると、圧側減衰バルブ２に設定通りの減衰力
の発生を期待できなくなる危惧がある。However, in the above proposal, when the piston speed is in the low speed range to the medium speed range, it is expected that the compression side damping valve 2 will generate the damping force as set. If the speed exceeds the middle speed range and reaches a particularly high speed range, there is a fear that the compression side damping valve 2 cannot be expected to generate the damping force as set.
【０００７】即ち、上記のピストン体１の上端面たる圧
側のバルブシート面は、内周側固定部１１と外周側シー
ト部１２との間に環状の所謂流路を形成するから、これ
に呼応するように圧側減衰バルブ２における受圧面が環
状になる。That is, the pressure side valve seat surface, which is the upper end surface of the piston body 1, forms an annular so-called flow path between the inner peripheral side fixed portion 11 and the outer peripheral side seat portion 12, and accordingly, this corresponds. As described above, the pressure receiving surface of the compression side damping valve 2 has an annular shape.
【０００８】従って、圧側減衰バルブ２を形成している
リーフバルブは、その外周端が全周に亙って撓むことに
なり、例えば、ピストン速度が低速域から中速域にある
ときには、圧側減衰バルブ２に設定通りの減衰力の発生
を期待できることになる。Therefore, the leaf valve forming the compression side damping valve 2 has its outer peripheral end bent over the entire circumference. For example, when the piston speed is in the low speed range to the medium speed range, the compression side is selected. The damping valve 2 can be expected to generate a damping force as set.
【０００９】しかし、圧側減衰バルブ２の外周端が全周
に亙って撓むことは、ピストン速度が中速域を過ぎて高
速域になっても同様であり、従って、このことから、圧
側減衰バルブ２の外周端が言わば撓み過ぎの状態にな
り、却って、所望の大きさの減衰力発生が期待できなく
なる。However, the fact that the outer peripheral end of the compression side damping valve 2 bends over the entire circumference is the same even when the piston speed goes beyond the medium speed range to the high speed range. Therefore, from this fact, The outer peripheral end of the damping valve 2 is, as it were, excessively bent, and on the contrary, it is not possible to expect a desired level of damping force generation.
【００１０】そして、ピストン速度の高速域における圧
側減衰バルブ２の撓み過ぎを防止するために、例えば、
リーフバルブの板厚を大きくする等して剛性を高めるよ
うにする場合には、ピストン速度の低速域から中速域の
圧側減衰力が全般的に高くなる上に、特に、初期減衰力
が異常に高くなる等の不具合を招くことになる。In order to prevent the compression side damping valve 2 from excessively bending in the high speed range of the piston speed, for example,
When increasing the leaf valve thickness to increase the rigidity, the damping force on the compression side generally increases from the low speed region to the medium speed region of the piston speed, and especially the initial damping force is abnormal. This will lead to problems such as high cost.
【００１１】そこで、この発明は、前記した事情を鑑み
て創案されたものであって、その目的とするところは、
油圧緩衝器におけるピストン速度の低速域から中速域の
減衰力を変更させることなく、ピストン速度が高速域に
なっても所定の大きさの減衰力の発生を可能にし、油圧
緩衝器のピストン部を形成するピストン体への利用に最
適となるバルブシート面構造を提供することである。Therefore, the present invention was devised in view of the above-mentioned circumstances, and its purpose is to:
The piston part of the hydraulic shock absorber can generate a predetermined amount of damping force even when the piston speed is in the high speed range without changing the damping force in the low speed range to the middle speed range of the hydraulic shock absorber. It is to provide a valve seat surface structure that is most suitable for use in a piston body that forms a valve.
【００１２】[0012]
【課題を解決するための手段】上記した目的を達成する
ために、この発明の構成を、シリンダ内で摺動するピス
トン部を形成のピストン体における端面たるバルブシー
ト面が減衰バルブの内周端を定着させる内周側固定部
と、減衰バルブの外周端を離着座させる外周側シート部
と、該外周側シート部と内周側固定部との間に形成され
て複数のポートのそれぞれの一端を開口せる開口部と、
外周側シート部と内周側固定部との間に形成されて各開
口部を相互に連通する連通部とを有し、減衰バルブにお
ける受圧面が環状になるバルブシート面構造において、
内周側固定部の外側に一端を連設した複数の遮蔽部を円
周方向に沿って配設し、各遮蔽部の他端と外周側シート
部との間に制限通路を形成し、ピストン速度が低速域か
ら中速域にあるときは作動油が制限通路を介して開口部
から連通部に流入し、ピストン速度が中速域から高速域
にあるときは作動油の流れが前記制限通路で制限される
ようにした。 In order to achieve the above object, the present invention has a structure in which a valve seat surface, which is an end surface of a piston body forming a piston portion sliding in a cylinder, is an inner peripheral end of a damping valve. An inner peripheral side fixing part for fixing the outer peripheral end of the damping valve, and an outer peripheral side seat part for seating the outer peripheral end of the damping valve, and one end of each of a plurality of ports formed between the outer peripheral side seat part and the inner peripheral side fixing part. An opening to open the
The damping valve has a communication part formed between the outer peripheral side seat part and the inner peripheral side fixed part and communicating the respective openings with each other .
In the valve seat surface structure in which the pressure receiving surface is
Circle multiple shields, one end of which is connected to the outside of the inner fixed part.
Arranged along the circumferential direction, the other end of each shielding part and the outer peripheral side sheet
A restricted passage is formed between the
When operating in the medium speed range from the
Flow into the communicating part from the piston speed of medium to high speed
The flow of hydraulic oil is restricted by the restriction passage when
I did it.
【００１３】同じく、他の手段は、シリンダ内で摺動す
るピストン部を形成のピストン体における端面たるバル
ブシート面が減衰バルブの内周端を定着させる内周側固
定部と、減衰バルブの外周端を離着座させる外周側シー
ト部と、該外周側シート部と内周側固定部との間に形成
されて複数のポートのそれぞれの一端を開口せる開口部
と、外周側シート部と内周側固定部との間に形成されて
各開口部を相互に連通する連通部とを有し、減衰バルブ
における受圧面が環状になるバルブシート面構造におい
て、外側シート部の内側に一端を連設した複数の遮蔽部
を円周方向に沿って配設し、各遮蔽部の他端と内周側固
定部の間に制限通路を形成し、ピストン速度が低速域か
ら中速域にあるときは作動油が制限通路を介して開口部
から連通部に流入し、ピストン速度が中速域から高速域
にあるときは作動油の流れが前記制限通路で制限される
ようにしたことを特徴とする。 Similarly, other means slide within the cylinder.
End face of the piston body forming the piston
The bushing surface secures the inner edge of the damping valve to the inner side.
Fixed part and the outer peripheral side seat that seats the outer peripheral edge of the damping valve.
Formed between the outer peripheral seat portion and the inner peripheral fixed portion
An opening that opens one end of each of the multiple ports
Is formed between the outer peripheral side seat part and the inner peripheral side fixed part.
A damping valve having a communication part that communicates each opening with each other.
The structure of the valve seat surface where the pressure receiving surface is annular.
, Multiple shields with one end connected inside the outer seat
Are arranged along the circumferential direction, and the other end of each shield and the inner peripheral side are fixed.
A restricted passage is formed between the fixed parts to check if the piston speed is in the low speed range.
When operating in the medium speed range from the
Flow into the communicating part from the piston speed of medium to high speed
The flow of hydraulic oil is restricted by the restriction passage when
It is characterized by doing so.
【００１４】[0014]
【発明の実施の態様】以下、図示した実施の態様に基づ
いてこの発明を説明するが、この発明に係るバルブシー
ト面構造も、これが具現化されるのは、前記した図３を
借りて説明すれば、油圧緩衝器のピストン部Ｐを形成す
るピストン体１における同図中で上端面たる圧側のバル
ブシート面である。BEST MODE FOR CARRYING OUT THE INVENTION Hereinafter, the present invention will be described based on the illustrated embodiments, but the valve seat surface structure according to the present invention will also be embodied by referring to FIG. 3 described above. That is, the valve seat surface on the pressure side, which is the upper end surface in the figure, of the piston body 1 forming the piston portion P of the hydraulic shock absorber.
【００１５】そして、この発明に係るバルブシート面構
造にあっても、上記バルブシート面は、図１に示すよう
に、圧側減衰バルブ２（図３参照）の内周端を定着させ
る内周側固定部１１と、圧側減衰バルブ２の外周端を離
着座させる外周側シート部１２と、該外周側シート部１
２と内周側固定部１１との間に形成されて複数の圧側ポ
ート１３（図３参照）のそれぞれの一端を開口させる開
口部１４と、外周側シート部１２と内周側固定部１１と
の間に形成されて各開口部１４を相互に連通させる連通
部１５と、を有してなる。Even in the valve seat surface structure according to the present invention, as shown in FIG. 1, the valve seat surface has an inner peripheral side on which the inner peripheral end of the compression side damping valve 2 (see FIG. 3) is fixed. The fixed portion 11, the outer peripheral seat portion 12 for seating the outer peripheral end of the compression side damping valve 2 on and off, and the outer peripheral seat portion 1
2 and the inner peripheral side fixed part 11 and the opening part 14 which opens each one end of the several compression side port 13 (refer FIG. 3), the outer peripheral side seat part 12, and the inner peripheral side fixed part 11. And a communication portion 15 that is formed between the openings 14 and connects the openings 14 to each other.
【００１６】因に、図示する実施の態様にあっても、ピ
ストン体１は、圧側ポート１３の上流側端を下端面たる
伸側のバルブシート面に開口させ、上端側の外周面とさ
れる傾斜面に伸側ポート１６の上流側端を開口させ、該
伸側ポート１６の下流側端を伸側のバルブシート面に離
着座可能に隣接された伸側減衰バルブ３に対向させると
している（図３参照）。Even in the illustrated embodiment, the piston body 1 has the upstream end of the compression side port 13 opened to the extended side valve seat surface which is the lower end surface, and is formed as the outer peripheral surface on the upper end side. The upstream side end of the expansion side port 16 is opened on the inclined surface, and the downstream side end of the expansion side port 16 is opposed to the expansion side damping valve 3 which is adjacent to the expansion side valve seat surface so as to be separably seated (( (See FIG. 3).
【００１７】ところで、該バルブシート面は、この発明
にあって、開口部１４と連通部１５との間に形成されて
開口部１４から連通部１５に向けての作動油の通過を制
御する遮蔽部１７を有してなるとしている。In the present invention, the valve seat surface is formed between the opening portion 14 and the communication portion 15, and is a shield for controlling passage of the hydraulic oil from the opening portion 14 toward the communication portion 15. It has a part 17.
【００１８】即ち、該遮蔽部１７は、ピストン速度が低
速域から中速域にあるときには、開口部１４から連通部
１５に向けての作動油の通過を許容するが、ピストン速
度が中速域から高速域にあるときには、開口部１４から
連通部１５に向けての作動油の通過を阻止するように作
用する。That is, when the piston speed is in the low speed range to the medium speed range, the shielding section 17 allows passage of the hydraulic oil from the opening section 14 toward the communication section 15, but the piston speed is in the medium speed range. When the vehicle is in the high speed range, it acts so as to prevent passage of the hydraulic oil from the opening portion 14 toward the communication portion 15.
【００１９】そして、該遮蔽部１７は、連通部１５の開
口部１４に近隣する縁部に一体に形成されてなるもの
で、図示する実施の態様では、一端が内周側固定部１１
に連設されるに対して他端が外周側シート部１２と分離
させてなるとし、該他端とこれが対向する外周側シート
部１２との間に制限通路Ｒを出現させるように形成され
ている。The shielding portion 17 is formed integrally with the edge portion of the communicating portion 15 adjacent to the opening portion 14. In the illustrated embodiment, one end is fixed to the inner peripheral side fixing portion 11.
The other end is separated from the outer peripheral side sheet portion 12, and the restriction passage R is formed between the other end and the outer peripheral side sheet portion 12 facing the other end. There is.
【００２０】因に、遮蔽部１７は、圧側減衰バルブ２の
静止時、即ち、圧側減衰バルブ２が該バルブシート面に
着座されているときに、その端面を圧側減衰バルブ２に
シートさせるように、即ち、内周側固定部１１及び外周
側シート部１２と同じ高さになるように設定されてい
る。Incidentally, the shielding portion 17 causes the end surface of the compression side damping valve 2 to be seated by the compression side damping valve 2 when the compression side damping valve 2 is stationary, that is, when the compression side damping valve 2 is seated on the valve seat surface. That is, the height is set to be the same as that of the inner peripheral side fixing portion 11 and the outer peripheral side seat portion 12.
【００２１】また、遮蔽部１７は、その配在方向が作動
油の所謂流出方向に沿うように、該バルブシート面にお
いて略放射方向に設定されている。Further, the shielding portion 17 is set in a substantially radial direction on the valve seat surface so that the distribution direction thereof is along the so-called outflow direction of the hydraulic oil.
【００２２】以上のように、バルブシート面に遮蔽部１
７が形成されて制限通路Ｒが出現されるように構成され
ることで、シリンダＣ内をピストン部Ｐが下降する該油
圧緩衝器の圧側作動時であって、ピストン速度が低速域
から中速域にあるときには、圧側ポート１３を介しての
開口部１４からの作動油は、制限通路Ｒを介して連通部
１５に流入しながら、圧側減衰バルブ２の外周側端と外
周側シート部１２との間を介して外部に流出することに
なり、従って、圧側減衰バルブ２は全周で均等に撓む状
態になる。As described above, the shield portion 1 is provided on the valve seat surface.
7 is formed so that the restriction passage R appears, so that when the hydraulic shock absorber operates such that the piston portion P descends in the cylinder C, the piston speed changes from a low speed range to a medium speed. In the region, the hydraulic oil from the opening 14 via the pressure side port 13 flows into the communication portion 15 via the restriction passage R, and while flowing into the outer peripheral side end of the pressure side damping valve 2 and the outer peripheral side seat portion 12. Therefore, the compression-side damping valve 2 is flexed uniformly over the entire circumference.
【００２３】それに対して、同じく圧側作動時でありな
がら、ピストン速度が中速域から高速域になるときに
は、圧側ポート１３を介しての開口部１４からの作動油
は、制限通路Ｒを容易には通過し得なくなり、従って、
連通部１５への流入量が減り、圧側減衰バルブ２の外周
側端と外周側シート部１２との間を介して外部に流出す
るとき、その多くが開口部１４に近いところから外部に
流出することになる。On the other hand, when the piston speed is changed from the medium speed range to the high speed range even during the pressure side operation, the hydraulic oil from the opening 14 via the pressure side port 13 easily flows through the restriction passage R. Cannot be passed through, therefore
When the amount of inflow into the communication portion 15 is reduced and flows out to the outside through the space between the outer peripheral side end of the compression side damping valve 2 and the outer peripheral side seat portion 12, most of it flows out from a place near the opening 14. It will be.
【００２４】その結果、圧側減衰バルブ２は、開口部１
４に近いところが大きく撓み、連通部１５に近いところ
が余り撓まない状態になり、このときに、大きい減衰力
が発生されることになる。As a result, the compression side damping valve 2 has the opening 1
A portion near 4 is largely bent, and a portion near the communicating portion 15 is not so much bent, and at this time, a large damping force is generated.
【００２５】また、上記の圧側作動から反転してシリン
ダＣ内をピストン部Ｐが上昇する該油圧緩衝器の伸側作
動時には、圧側減衰バルブ２は、外周側シート部１２に
着座するのは勿論であるが、制限通路Ｒを形成する遮蔽
部１７にも着座することになり、このとき、遮蔽部１７
が略放射方向に形成されていて圧側減衰バルブ２を所謂
裏側から支える状態になり、従って、該圧側減衰バルブ
２における着座時の撓み防止を効果的に防止し得ること
になる。When the hydraulic shock absorber is operated in the expansion side in which the piston portion P rises in the cylinder C by reversing from the pressure side operation, the compression side damping valve 2 is of course seated on the outer peripheral side seat portion 12. However, the user also sits on the shielding portion 17 forming the restricted passage R, and at this time, the shielding portion 17
Is formed in a substantially radial direction to support the compression-side damping valve 2 from the so-called back side, and therefore, it is possible to effectively prevent the compression-side damping valve 2 from bending when seated.
【００２６】図２は、この発明の他の実施の態様に係る
バルブシート面構造を示すもので、この実施の態様にお
けるバルブシート面に形成の遮蔽部１７は、一端を内周
側固定部１１と分離させるに対して他端を外周側シート
部１２に連設させるとし、該他端と内周側固定部１１と
の間に制限通路Ｒを出現させるとしている。FIG. 2 shows a valve seat surface structure according to another embodiment of the present invention. The shield portion 17 formed on the valve seat surface in this embodiment has one end fixed to the inner peripheral side fixing portion 11. In contrast to the above, the other end is connected to the outer peripheral side sheet portion 12, and the restricted passage R appears between the other end and the inner peripheral side fixing portion 11.
【００２７】この実施の態様による場合には、前記した
図１に示す実施の態様に比較して、制限通路Ｒが所謂内
周側に形成されるから、遮蔽部１７による遮蔽効果が大
きくなり、従って、より大きい減衰力の発生を期待でき
ると共に、伸側への反転時の圧側減衰バルブ２における
外周端側の撓み防止に有利となる利点がある。In the case of this embodiment, as compared with the embodiment shown in FIG. 1, the limiting passage R is formed on the so-called inner peripheral side, so that the shielding effect by the shielding portion 17 becomes large, Therefore, there is an advantage that a larger damping force can be expected and it is advantageous in preventing the deflection of the outer peripheral end side of the compression side damping valve 2 when reversing to the extension side.
【００２８】前記したところは、バルブシート面が圧側
減衰バルブが隣接される圧側のバルブシート面とされる
場合を例にしたが、この発明の意図するところからすれ
ば、バルブシート面が伸側減衰バルブが隣接される伸側
のバルブシート面とされる場合であっても同様であり、
その場合の作用効果も同様である。The above description has been made by taking the case where the valve seat surface is the valve seat surface on the compression side adjacent to the compression side damping valve, but from the intent of the present invention, the valve seat surface is the expansion side. The same applies when the damping valve is the adjacent valve seat surface on the extension side,
The effect in that case is also the same.
【００２９】[0029]
【発明の効果】以上のように、この発明にあっては、ピ
ストン速度が低速域から中速域にあるときに減衰バルブ
の全周撓みで所定の大きさの減衰力発生を可能にする一
方で、ピストン速度が中速域から高速域になるときに
は、減衰バルブの部分的な撓みで所定の大きさの減衰力
発生を可能にするから、中速域以上になっても全周撓み
が現出されて所定の大きさの減衰力発生を期待できなく
なるサチュレート現象の防止に有効となる利点がある。As described above, according to the present invention, when the piston speed is in the low speed range to the middle speed range, it is possible to generate the damping force of a predetermined magnitude by the entire circumference deflection of the damping valve. Thus, when the piston speed changes from the medium speed range to the high speed range, the partial deflection of the damping valve enables the generation of a damping force of a predetermined magnitude. There is an advantage that it is effective in preventing the saturating phenomenon in which it is not possible to expect a damping force of a predetermined magnitude to be generated.
【００３０】また、この発明にあっては、一方側の作動
から反転して減衰バルブがバルブシート面に着座すると
きに、制限通路を形成する遮蔽部にも着座することにな
り、このとき、遮蔽部が減衰バルブを所謂裏側から支え
る状態になり、従って、該減衰バルブにおける着座時の
撓みを効果的に防止し、該減衰バルブの耐久性を向上さ
せることになる利点がある。Further, according to the present invention, when the damping valve is seated on the valve seat surface by reversing from the operation on the one side, the seat is also seated on the shielding portion forming the restriction passage. The shield portion supports the damping valve from the so-called back side, so that there is an advantage that the bending of the damping valve at the time of sitting is effectively prevented and the durability of the damping valve is improved.
【図面の簡単な説明】[Brief description of drawings]
【図１】この発明の一実施の態様に係るバルブシート面
構造のピストン体におけるバルブシート面を示す端面図
である。FIG. 1 is an end view showing a valve seat surface of a piston body having a valve seat surface structure according to an embodiment of the present invention.
【図２】他の実施の態様に係るバルブシート面構造のピ
ストン体におけるバルブシート面を示す端面図である。FIG. 2 is an end view showing a valve seat surface of a piston body having a valve seat surface structure according to another embodiment.
【図３】従来例としての油圧緩衝器におけるピストン部
分を示す縦断面図である。FIG. 3 is a vertical sectional view showing a piston portion of a hydraulic shock absorber as a conventional example.
【図４】従来例としての図３のピストン体におけるバル
ブシート面を図１と同様に示す図である。FIG. 4 is a view showing a valve seat surface of the piston body of FIG. 3 as a conventional example, similar to FIG. 1.
Ｃ シリンダ Ｌ 圧側油室 Ｐ ピストン部 Ｒ 制限通路 Ｕ 伸側油室 １ ピストン体 ２ 圧側減衰バルブ ３ 伸側減衰バルブ １１ 内周側固定部 １２ 外周側シート部 １３ 圧側ポート １４ 開口部 １５ 連通部 １６ 伸側ポート １７ 遮蔽部 C cylinder L pressure side oil chamber P piston part R restricted passage U Extension side oil chamber 1 piston body 2 Pressure side damping valve 3 Extension side damping valve 11 Inner peripheral side fixed part 12 Outer peripheral side sheet 13 Pressure side port 14 openings 15 Communication 16 Extension side port 17 Shield
フロントページの続き (58)調査した分野(Int.Cl.7，ＤＢ名) F16F 9/348 Continuation of front page (58) Fields surveyed (Int.Cl. 7 , DB name) F16F 9/348
Claims (2)
のピストン体における端面たるバルブシート面が減衰バ
ルブの内周端を定着させる内周側固定部と、減衰バルブ
の外周端を離着座させる外周側シート部と、該外周側シ
ート部と内周側固定部との間に形成されて複数のポート
のそれぞれの一端を開口せる開口部と、外周側シート部
と内周側固定部との間に形成されて各開口部を相互に連
通する連通部とを有し、減衰バルブにおける受圧面が環
状になるバルブシート面構造において、内周側固定部の
外側に一端を連設した複数の遮蔽部を円周方向に沿って
配設し、各遮蔽部の他端と外周側シート部との間に制限
通路を形成し、ピストン速度が低速域から中速域にある
ときは作動油が制限通路を介して開口部から連通部に流
入し、ピストン速度が中速域から高速域にあるときは作
動油の流れが前記制限通路で制限されるようにしたこと
を特徴とするバルブシート面構造1. An inner peripheral side fixed part for fixing an inner peripheral end of a damping valve by a valve seat surface, which is an end face of a piston body forming a piston part sliding in a cylinder, and an outer peripheral end of the damping valve are seated separately. An outer peripheral side seat portion; an opening formed between the outer peripheral side seat portion and the inner peripheral side fixed portion to open one end of each of the plurality of ports; and an outer peripheral side seat portion and an inner peripheral side fixed portion. And a communication part that is formed between them and connects the openings to each other, and the pressure receiving surface of the damping valve is a ring.
In the valve seat surface structure becomes Jo, the inner peripheral side fixing portion
A plurality of shields with one end connected to the outside along the circumferential direction
Installed and restricted between the other end of each shield and the outer peripheral seat
A passage is formed and the piston speed is in the low to medium speed range.
The hydraulic oil flows from the opening to the communicating part through the restricted passage.
When the piston speed is in the middle to high speed range,
The flow of hydraulic fluid is restricted by the restriction passage.
Valve seat surface structure characterized by
のピストン体における端面たるバルブシート面が減衰バ
ルブの内周端を定着させる内周側固定部と、減衰バルブ
の外周端を離着座させる外周側シート部と、該外周側シ
ート部と内周側固定部との間に形成されて複数のポート
のそれぞれの一端を開口せる開口部と、外周側シート部
と内周側固定部との間に形成されて各開口部を相互に連
通する連通部とを有し、減衰バルブにおける受圧面が環
状になるバルブシート面構造において、外側シート部の
内側に一端を連設した複数の遮蔽部を円周方向に沿って
配設し、各遮蔽部の他端と内周側固定部の間に制限通路
を形成し、ピストン速度が低速域から中速域にあるとき
は作動油が制限通路を介して開口部から連通部に流入
し、ピストン速度が中速域から高速域にあるときは作動
油の流れが前記制限通路で制限されるようにしたことを
特徴とするバルブシート面構造2. A piston portion that slides in a cylinder is formed.
The valve seat surface, which is the end surface of the piston body of
Inner peripheral side fixing part to fix inner peripheral edge of lube and damping valve
The outer peripheral side seat part for separating and seating the outer peripheral end of the
Multiple ports that are formed between the inner part and the inner peripheral side fixed part
The opening that opens one end of each of the
Is formed between the inner peripheral side fixed part and the inner peripheral side fixed part so that the openings are connected to each other.
And the pressure receiving surface of the damping valve is a ring.
In the valve seat surface structure that becomes a shape,
A plurality of shields with one end connected to the inside along the circumferential direction
Disposed between the other end of each shielding part and the inner peripheral side fixed part.
When the piston speed is in the low to medium speed range
Causes hydraulic oil to flow from the opening into the communication part through the restricted passage
However, it operates when the piston speed is in the medium to high speed range.
That the oil flow is restricted by the restriction passage
Characteristic valve seat surface structure
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP24242195A JP3516106B2 (en) | 1995-08-28 | 1995-08-28 | Valve seat surface structure |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP24242195A JP3516106B2 (en) | 1995-08-28 | 1995-08-28 | Valve seat surface structure |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH0960681A JPH0960681A (en) | 1997-03-04 |
| JP3516106B2 true JP3516106B2 (en) | 2004-04-05 |
Family
ID=17088871
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP24242195A Expired - Fee Related JP3516106B2 (en) | 1995-08-28 | 1995-08-28 | Valve seat surface structure |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3516106B2 (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2015177880A1 (en) * | 2014-05-20 | 2015-11-26 | 株式会社ショーワ | Pressure cushioning device and damping force generation member |
-
1995
- 1995-08-28 JP JP24242195A patent/JP3516106B2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0960681A (en) | 1997-03-04 |
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