JP2006220252A - Two-stage pressure absorption piston-type accumulator device - Google Patents

Two-stage pressure absorption piston-type accumulator device Download PDF

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JP2006220252A
JP2006220252A JP2005035939A JP2005035939A JP2006220252A JP 2006220252 A JP2006220252 A JP 2006220252A JP 2005035939 A JP2005035939 A JP 2005035939A JP 2005035939 A JP2005035939 A JP 2005035939A JP 2006220252 A JP2006220252 A JP 2006220252A
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pressure
piston
high
oil
accumulator
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JP4759282B2 (en
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Masao Nakamura
Atsushi Yoshimoto
正男 中村
厚 吉本
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Nakamura Koki Kk
中村工機株式会社
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Abstract

<P>PROBLEM TO BE SOLVED: To miniaturize a low-pressure/high-pressure combined accumulator device, and realize stable behavior of a piston for high pressure at the time of transition from a low-pressure stage to a high-pressure stage. <P>SOLUTION: A structure 2 of a high pressure accumulator is formed on one side of a divider member 6, which is a boundary, and a structure 4 of a low pressure accumulator is formed on the other side of the divider member 6. Then oil chambers 11, 12 are demarcated between the pistons 3, 5 of each of the accumulator structures 2, 4 and the divider member 6, and gas chambers 17, 18 are demarcated between the pistons 3, 5 and each of the end covers 9, 10. Then a communicating passage 13 is formed in the divider member 6. The communicating passage 13 connects each of the oil chambers 11, 12 to an exterior hydraulic circuit, and performs supply and discharge of hydraulic oil in accordance with the ascent/descent of the circuit pressure. Then a small-diameter boss part 19 is projected on the oil chamber side of the piston 3 for high pressure, and a fitting recess 20 for the in-and-out movement of the small-diameter boss part 19 is provided to the opening of the communicating passage 13, thus a piston load caused by upsurged pressure oil is reduced. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

本発明は二段圧吸収式ピストン型アキュムレータ装置に係り、詳しくは油圧回路において変動した圧力の作動油を低圧時と高圧時で異なるばね定数に基づき給排させることができるようにした複合アキュムレータ装置に関するものである。 The present invention relates to a two-stage pressure-absorbing piston type accumulator, details composite accumulator apparatus which can be based supply and discharge to different spring constant hydraulic oil pressure which is varied in the hydraulic circuit at the time of low pressure at a high pressure it relates.

油圧モータや油圧シリンダといったアクチュエータに油圧ポンプからの油圧油を供給して作動させる油圧回路においては、アクチュエータに大きな負荷が掛かったりロック状態に陥ったりすると回路圧が正常運転時より上昇する。 In the hydraulic oil hydraulic circuit for operating by supplying from the hydraulic pump to the actuator such as a hydraulic motor or hydraulic cylinder, circuit pressure if a large load on the actuator or fallen into applied or locked state rises above normal operation. このとき油圧回路に接続されたアキュムレータは回路の流通油を吸収してアクチュエータに掛かる負荷を和らげ、またアクチュエータのロック状態が解除されるなどすると吸収油を吐出して、油圧ポンプからの送給油の遅れを補う。 At this time accumulator connected to the hydraulic circuit relieve the load applied to the actuator to absorb the circulation oil circuit, also by ejecting an absorption oil to such locked state of the actuator is released, the oil feed from the hydraulic pump compensate for the delay. このように、アキュムレータは、油室に進入してくる作動油の圧力に応じて、ガス室に封入したガスの容積を収縮させて圧力バランスを図り、油圧回路の圧力調整作用を果たす。 Thus, the accumulator, according to the pressure of the hydraulic oil coming enters the oil chamber, while contracting the volume of the gas sealed in the gas chamber aims to pressure balance, performs a pressure adjustment operation of the hydraulic circuit.

ところが、油圧回路で発生した急激な圧力の上昇を一つのアキュムレータによって吸収させる場合のほかに、例えば車両のサスペンション機構などにおけるように、作動油圧の大きさを二段階に分けて二つのアキュムレータにより圧油を吸収させようとする場合がある。 However, pressure in addition to the case to be absorbed by one of the accumulators rapid increase in pressure generated in the hydraulic circuit, for example, such as in a vehicle suspension mechanism, the two accumulators the size of the working oil pressure in two steps there is a case to try to absorb the oil. すなわち、搭乗者が少ないときには軟らかい乗り心地を発揮させるべくばね定数の低いアキュムレータを機能させ、搭乗者数が多い場合や積荷が重い場合には高いばね定数を発揮するアキュムレータを動作させて支持力を強める。 That is, the passenger is made to function with low accumulator spring constant in order to exert a soft ride when small, the by operating an accumulator which exerts a high spring constant in the case or if the cargo number of passengers is often heavy supporting force ramp up.

このようにアキュムレータを二基またはそれ以上を採用し、それらを使い分けることが例えば特開2004−360885や特表2004−522905にも記載されている。 Thus the accumulator employs a second base, or more, it is also described in that selectively them, for example, JP-2004-360885 and JP-T 2004-522905. 図13および図14は、二つの組合せアキュムレータの動きを示したものである。 13 and 14 shows the movement of the two combined accumulator. 図14の(a)に示すごとく、高圧用アキュムレータ51と低圧用アキュムレータ52とからなり、その各油室53,54は図示しない油圧回路に繋がる主管55に対して、枝管56,57を介して連通されている。 As shown in (a) of FIG. 14, consists of a high-pressure accumulator 51 and a low pressure accumulator 52, the respective oil chambers 53 and 54 with respect to the main pipe 55 which leads to a hydraulic circuit (not shown), through a branch pipe 56, 57 It is communicated with each other Te.

高圧用アキュムレータ51のガス室58には予め例えば5MPaの不活性ガスが、低圧用アキュムレータ52のガス室59には例えば2.5MPaのガスが装入栓60,61を介して封入される。 Pre e.g. 5MPa of the inert gas in the gas chamber 58 of the high-pressure accumulator 51, for example 2.5MPa gas into the gas chamber 59 of the low pressure accumulator 52 is filled via the instrumentation Nyusen 60,61. 管路55が油圧回路に接続される前の状態では、図13の(a)のように、いずれのピストン62,63もガス圧により、各装入栓から最も離れたところに位置する。 In a state before the pipe 55 is connected to the hydraulic circuit, as shown in (a) of FIG. 13, by any of the piston 62, 63 is also gas pressure, is located furthest from KakuSo Nyusen.

接続された油圧回路での低圧段階の正常運転圧が例えば3MPa前後であると、低圧用ピストン63は図示しないが導入油を油室54に収容すべくガス室59を少し縮めて圧力バランスが得られる位置まで変位する。 When normal operating pressure of the low pressure stage of the connected hydraulic circuit for example before and after 3 MPa, little shrink pressure balance is obtained a gas chamber 59 to accommodate the The introducing oil low-pressure piston 63 is not shown in the oil chamber 54 It is displaced to a position that is. その状態にあるとき一時的に4.5MPaまで昇圧したとすると、図13の(b)のように低圧用ピストン63はガス室59をさらに縮めて変位する。 When the boosted until temporarily 4.5MPa when in that state, the low-pressure piston 63 as shown in (b) of FIG. 13 is displaced further shrink the gas chamber 59. それによって油室54は追加的に作動油を受け入れ、油圧回路における油量が油室54へ進入した分だけ減少し、回路圧を降下させる。 Whereby the oil chamber 54 accepts the additional hydraulic oil, and decreased by the amount of oil in the hydraulic circuit enters into the oil chamber 54, lowering the circuit pressure. この昇圧が一時的なものでその後に降下すれば、封入ガスの膨張によりピストン63が押し戻され、追加導入分が油圧回路へ返される。 If the booster is subsequently lowered in temporary, piston 63 is pushed back by the expansion of the filler gas, additional introduction amount is returned to the hydraulic circuit.

今述べた4.5MPaの圧力が一時的なものでなく、上記したサスペンション機構の例でいえば積荷によるものであるとすると、その荷物が降ろされるまではこの圧力が高圧段階における定常運転圧となる。 Not pressure 4.5MPa mentioned is temporary Assuming that is due to the cargo in the example of the suspension mechanism as described above, until the load is lowered and the steady operating pressure the pressure in the high pressure stage Become. このとき、5MPaのガス室58を持つ高圧用アキュムレータ51のピストン62は、依然として初期位置にとどまる。 At this time, the piston 62 of the high-pressure accumulator 51 with 5MPa gas chamber 58 is still remains in the initial position. この状態は、油圧回路で5MPa以上の圧力が立つまで変わることはないが、積荷が重くて7.5MPaであったとすると、図14の(a)のように低圧用ピストン63がさらに左行すると共に、高圧用ピストン62はその圧力にバランスする位置まで変位する。 This state is never changed to 5MPa or more pressure hydraulic circuit stand, the cargo is to have been 7.5MPa heavy, further leftward low pressure piston 63 as in (a) of FIG. 14 with, high-pressure piston 62 is displaced to a position to balance the pressure.

荷物積載により高圧段階に入っている状態で油圧回路圧が10MPaまで一時的に上昇したとすると、図14の(b)のように高圧用ピストン62がガス室58をさらに縮めるべく変位する。 When the hydraulic circuit pressure in a state contained in the high pressure stage by cargo loading is to temporarily rises to 10 MPa, the high pressure piston 62 as shown in (b) of FIG. 14 is displaced to further shorten the gas chamber 58. なお、低圧用ピストン63もこのときのバランス圧に到達するまでガス室59を縮める。 Note that reducing the gas chamber 59 to be the low pressure piston 63 reaches the balance pressure at this time.

いずれのアキュムレータにおいても油室に作動油を受け入れることになるが、高圧段階においては、低圧用アキュムレータ52での増加量が高圧用アキュムレータ51におけるそれに比べて少ない。 Although will accept hydraulic oil to the oil chamber in any of the accumulator, in the high-pressure stage, the amount of increase in the low-pressure accumulator 52 is smaller than that in the high-pressure accumulator 51. この例では、高圧段階における油量吸収の約2/3は高圧用アキュムレータが担うことになり、概して、低圧用ピストンの動きは低圧段階での昇圧軽減に寄与し、高圧用ピストンは高圧段階での昇圧抑制に貢献する。 In this example, about 2/3 of the amount of oil absorption in the high-pressure stage will be responsible high-pressure accumulator, generally, movement of the low pressure piston contributes to boosting mitigation at low pressure stage, high pressure piston at high pressure stage to contribute to the step-up suppression. この場合、サスペンション機構は、低圧時と高圧時で異なるばね定数に基づいた支持特性を発揮することになる。 In this case, the suspension mechanism would exert supporting characteristics based on different spring constants at low pressure at a high pressure.
特開2004−360885 Patent 2004-360885 特表2004−522905 JP-T 2004-522905

このような組合せアキュムレータによれば、油圧回路に発生した一時的な圧力上昇を吸収するため、作動油圧の大きさに応じて二段階に分けて圧油収容量を変更し、油圧回路における低圧段階および高圧段階それぞれにおける昇圧を軽減することができる。 According to such a combination accumulator for absorbing transient pressure increase that occurred in the hydraulic circuit, by changing the pressure oil storage amount in two stages in accordance with the magnitude of the hydraulic pressure, the low pressure stage in the hydraulic circuit and it is possible to reduce the boost in each pressure stage. しかし、アキュムレータが二基であり、またそれ以上の基数を必要とする場合には装置としての嵩張りが甚だしくなる。 However, the accumulator is a two-group, also bulky becomes unduly of the apparatus in the case of requiring more radix. 例えばサスペンション機構で採用しようとすると、車両への搭載性の観点から、その小型化の命題解決は不可欠となる。 For example, if you try to employ in the suspension mechanism, in view of mountability to vehicle, proposition solve the miniaturization is essential.

ところで、一つの油圧回路が低圧段階と高圧段階とをとる系である場合、その切り替わり目で問題が生じる。 Incidentally, if one of the hydraulic circuit is a system that takes the low-pressure stage and high pressure stage, problems occur in that switching point. それは、高圧用アキュムレータが動作を開始する前後の圧油、上記した例で言えば4.5MPaが高圧段階における定常圧となっている場合に、5MPaを急速に超えて昇圧していく場面や、5MPa前後を小幅に行き来する場面で遭遇する。 It and scenes high-pressure accumulator before and after the hydraulic fluid starts to operate, when 4.5MPa In the example described above is a constant pressure in the high pressure stage, continue to boost rapidly exceeded 5 MPa, encountered in the scene to be slightly back and forth back and forth 5MPa.

油圧回路圧が例えば7MPaへ急上昇した場合、ほとんど負荷の掛かっていなかった高圧用アキュムレータは急激に増大する負荷に襲われる。 If the hydraulic circuit pressure that jumped example to 7 MPa, most high-pressure accumulator has not been unloaded are attacked by the load increases rapidly. 今まで停止していた高圧用ピストンが進入する圧油の行く手を一時的に阻むことになり、進入油の圧力をさらに高める。 High pressure piston that has been stopped until now is that the arresting way of the pressure oil to the temporarily enters, further increasing the pressure of the incoming oil. 急動作が強いられるピストンは、これに原因してガス室側に圧力波を発生させる。 Piston quick operation is strong, which causes to generate a pressure wave in the gas chamber side. 波はガス室内を高速で往復伝播するから、ピストンのシール機構が断続的に加振されたり圧力衝撃波を受け、シール耐力の低下を早める。 Since the wave is round-trip propagation gas chamber at high speed, the piston of the sealing mechanism is intermittently subjected to pressure shock waves or is vibrated, hasten the deterioration of the sealing strength.

他方、低圧段階と高圧段階との切り替わり目で圧力が小刻みに変動する場合、ピストンがそれに過敏に追従するとピストンは動きはじめては戻るという動きを繰り返す。 On the other hand, when varying little by little pressure at switching point between the low-pressure stage and high pressure stage, the piston can follow sensitively thereto piston repeated motion that motion first returns. このようなチャタリングが発生すると、ピストンはその都度シェルカバーを叩く。 When such chattering occurs, the piston strikes the in each case shell cover. これによるピストン本体の損傷やピストンシール機構の損耗は、装置の信頼性を損ないまた頻繁な保守作業を要求することになる。 This by wear of the piston body damage or piston seal mechanism, it will require also frequent maintenance impair the reliability of the device.

本発明は上記の問題に鑑みなされたもので、その目的は、低圧用アキュムレータと高圧用アキュムレータを備えた複合アキュムレータ装置において、その装置全体が占める容積をアキュムレータが二基ある場合と同等に確保しながら小型化を可能にすること、油圧回路における低圧段階から高圧段階へもしくはその逆への切り替わり目における高圧用ピストンの穏やかな加減速を可能にしまた過敏な応答動作を抑止して、装置の信頼性や耐用性を向上させることを実現する二段圧吸収式ピストン型アキュムレータ装置を提供することである。 The present invention has been made in view of the above problems, its object is, in the composite accumulator having a low pressure accumulator and the high-pressure accumulator, to ensure the volume in its entirety device occupies the equivalent if the accumulator there are two groups allowing miniaturization while, to suppress to allow gentle acceleration and deceleration of the high pressure piston at switching point from the low pressure stage to the high pressure stage or vice versa the hypersensitive response operation in the hydraulic circuit, reliability of the device to provide a two-stage pressure-absorbing piston type accumulator to realize to improve the resistance and durability.

本発明は、油圧回路に発生した一時的な圧力上昇を吸収するため、作動油圧の大きさを二段階に分けて収容量を変更し、油圧回路における低圧段階および高圧段階それぞれにおける昇圧を軽減できるようにした複圧吸収可能なアキュムレータに適用される。 The present invention, in order to absorb a temporary pressure increase that occurred in the hydraulic circuit, the magnitude of the hydraulic pressure to change the storage capacity in two steps, can reduce the boost in each low-pressure stage and high pressure stage in the hydraulic circuit It applied to Fuku圧 absorbable accumulator as. その特徴とするところは、図1を参照して、仕切部材6を境にして一方の側に高圧用アキュムレータ構造2が、他方の側に低圧用アキュムレータ構造4が形成される。 And has as its features, with reference to FIG. 1, the high-pressure accumulator structure 2 on one side by a partition member 6 as a boundary, the low-pressure accumulator structure 4 is formed on the other side. 各アキュムレータ構造2,4のピストン3,5と仕切部材6との間に油室を、ピストン3,5とアキュムレータシェルの各端部カバー9,10との間にガス室17,18を画成させる。 Defining a gas chamber 17, 18 between the piston 3,5 and the oil chamber between the partition member 6, piston 3, 5 and the end cover 9, 10 of the accumulator shell of each accumulator structure 2,4 make. 仕切部材6には、各油室11,12と外部の油圧回路とを繋ぎ、回路圧の昇降に応じて作動油を給排させる連通路13が形成される。 The partition member 6, connecting the hydraulic circuit of the oil chambers 11 and 12 and the external communication passage 13 for supplying and discharging the hydraulic oil in response to the lifting of the circuit pressure are formed. 高圧用ピストン3の油室側には、小径ボス部19が連通路13の開口に向けて突出して形成され、高圧用油室11に臨む連通路13の開口部には小径ボス部19を出入りさせる嵌挿凹部20が設けられる。 The oil chamber side of the high-pressure piston 3, the small diameter boss portion 19 is formed to project toward the opening of the communication passage 13, and out of the small-diameter boss portion 19 in the opening of the communication passage 13 facing the high pressure oil chamber 11 insertion fitting recess portion 20 is provided to. これによって、低圧段階と高圧段階との切り替わり時の高圧用ピストン3を滑らかにまた安定して挙動させることができるようになる。 Thus, it is possible to smoothly also stable behavior of the high-pressure piston 3 when switching the low-pressure stage and high pressure stage.

図6に示すように、内筒部材31を境にして内方側に高圧用アキュムレータ構造2Aが形成され、外方側にリング状ピストン5Bを備えた低圧用アキュムレータ構造4Aを形成させるようにすることもできる。 As shown in FIG. 6, the high-pressure accumulator structure 2A is formed on the inner side by the inner cylindrical member 31 as a boundary, so as to form a low-pressure accumulator structure 4A having a ring-shaped piston 5B outward side it is also possible. その内筒部材31と外筒部材34を同心状に保持する一方の端部カバー32と各アキュムレータ構造2A,4Aのピストン3,5Bとの間に油室11A,12Aを、他方の端部カバー33とピストン3,5Bとの間にガス室17A,18Aを画成させる。 Its inner cylindrical member 31 and the outer tubular member 34 and one end cover 32 to hold concentrically the accumulators structure 2A, oil chamber 11A between the 4A piston 3,5B, the 12A, the other end cover gas chamber 17A between 33 and piston 3,5B, thereby defined the 18A. 一方の端部カバー32には、各油室11A,12Aと外部の油圧回路とを繋ぎ、回路圧の昇降に応じて作動油を給排させる連通路35が形成され、高圧用ピストン3の油室側には、小径ボス部19が連通路35の開口に向けて突出して形成される。 At one end the cover 32, the oil chambers 11A, connects the 12A and the external hydraulic circuit communication passage 35 for supplying and discharging the hydraulic oil in response to the lifting of the circuit pressure are formed, the oil of the high pressure piston 3 the chamber side, small-diameter boss portion 19 is formed to protrude toward the opening of the communication passage 35. そして、高圧用油室11Aに臨む連通路35の開口部には小径ボス部19を出入りさせる嵌挿凹部20が設けられ、低圧段階と高圧段階との切り替わり時の高圧用ピストン3を滑らかにまた安定して挙動させることができるようにしている。 The 挿凹 portion 20 fitted to and from the small diameter boss portion 19 is provided on the opening of the communication passage 35 facing the high pressure oil chamber 11A, smooth high pressure piston 3 when switching the low-pressure stage and high pressure stage also so that it is possible to stably behavior.

図1に戻って、小径ボス部19には、嵌挿凹部20を出入りするとき連通路13と高圧用油室11との間を移行する作動油量の増減を補助し、低圧段階から高圧段階へおよびその逆への遷移における高圧用ピストン3の動きをより一層滑らかにするための圧油給排路23を形成しておくとよい。 Returning to FIG. 1, the small diameter boss 19 assists to increase or decrease the amount of hydraulic oil to migrate between the communication passage 13 and the high pressure oil chamber 11 when out of the insertion fitting recess portion 20, the high-pressure stage from a low pressure stage f and may want to form a pressure oil supply and discharge passage 23 for the more smooth movement of the pressure piston 3 in the transition to the reverse.

図9に示すように、一方の端部カバー32に形成する連通路36は油圧回路と低圧用油室12Aとのみを繋ぐものであってもよい。 As shown in FIG. 9, the communication passage 36 formed in one end cover 32 may be one that connects only the hydraulic circuit and a low-pressure oil chamber 12A. その内筒部材31には、低圧用油室12Aと高圧用油室11Aとの間で作動油を流通させる直径の異なる透孔37が一方の端部カバー32の近傍に設けられる。 In that the inner tube member 31, is provided in the vicinity of the through holes 37 of different diameters for circulating hydraulic fluid between the low-pressure oil chamber 12A and the high pressure oil chamber 11A is one end cover 32. 透孔37a,37b,37cは、高圧用ピストン3Aが一方の端部カバー32の近くで変位するとき、両油室12A,11A間で移行する作動油量を滑らかに増減し、低圧段階と高圧段階との切り替わり時の高圧用ピストン3Aの挙動が安定したものとなるように、一方の端部カバー32に近接するにつれて孔径が小さく与えられる。 Holes 37a, 37b, 37c, when the high-pressure piston 3A is displaced near the one end cover 32, Ryoaburashitsu 12A, smoothly increase or decrease the amount of hydraulic oil to migrate between 11A, the low-pressure stage and a high pressure as the behavior of the high-pressure piston 3A when switching between stage becomes stable, pore size is given smaller as close to the one end cover 32. なお、図11のように、内筒部材31を境にして形成されるアキュムレータの低圧用と高圧用を逆にすることもできる。 Incidentally, as shown in FIG. 11, it is also possible to use low pressure and high pressure accumulator formed by an inner tubular member 31 as a boundary to the reverse.

例えば図3の(b)にあるように、高圧用油室11に通じる補助路24が設けられ、この補助路24に油圧急上昇時の初期圧油を高圧用油室11に導入するチェックバルブ25を介装させておくようにしてもよい。 For example, as in (b) of FIG. 3, the check valve 25 auxiliary passage 24 leading to the high pressure oil chamber 11 is provided for introducing the initial pressure oil at a hydraulic jump in the high pressure oil chamber 11 in the auxiliary passage 24 it may be allowed to interposed.

本発明によれば、仕切部材を境にして二つのアキュムレータを並べ、低圧用アキュムレータ構造も高圧用アキュムレータ構造も各油室を仕切部材側に配置し、それら油室と外部の油圧回路とを繋ぐ連通路を仕切部材に形成させるようにしたので、作動油圧の大きさを二段階に分けて収容量を変更し、油圧回路における低圧段階および高圧段階それぞれにおける昇圧を異なるばね定数のアキュムレータによって軽減することができる。 According to the present invention arranges two accumulator to the partition member as a boundary, even high pressure accumulator structure low-pressure accumulator structure also places each oil chamber on the partition member side, connect with their oil chamber and the outside of the hydraulic circuit since the communication path and so as to form the partition member, the size of the hydraulic pressure to change the storage capacity in two steps, to reduce the accumulator spring constant different boost in each low-pressure stage and high pressure stage in the hydraulic circuit be able to. そして、仕切部材を二つのアキュムレータのシェルカバーとして共用させることになり、複合アキュムレータとしての装置を短くし、サスペンション機構用などとして車載のための小型化を図ることができる。 Then, it becomes possible to share the partition member as a shell cover of the two accumulators, it is possible to shorten the device as a composite accumulator miniaturized for vehicle as such a suspension mechanism.

高圧用ピストンの油室側に突出して形成された小径ボス部と、高圧用油室に臨む連通路の開口部に設けた嵌挿凹部とを備えるので、油圧回路における低圧段階と高圧段階との切り替わり時のピストンの不安定挙動の発生を回避させることができる。 Since comprises a small diameter boss portion formed to protrude to the oil chamber side of the high pressure piston, and a 挿凹 portion fitting provided in the opening of the communication passage facing the high pressure oil chamber, the low-pressure stage and high pressure stage in the hydraulic circuit it is possible to avoid the occurrence of unstable behavior of the piston when pressed. 高圧用ピストンの着座・離座時の低加速度化や僅かな圧力変化に基づく過敏な挙動の抑制は、ピストンのみならず装置全体の信頼性、耐用性を高める。 Suppression of hypersensitivity behavior based on seating, unseated low acceleration reduction and slight pressure change at the time of high-pressure piston, the reliability of the whole as well piston only device, increasing the durability.

内筒部材を境にして内方側に高圧用アキュムレータ構造を、外方側にリング状ピストンを備えた低圧用アキュムレータ構造を形成させ、各アキュムレータのピストンとの間で油室を形成させる一方の端部カバーに連通路を形成し、これに小径ボス部が出入りする嵌挿凹部を設けるようにしても、高圧段階と低圧段階との間の切り替わり目における高圧用ピストンの過剰反応的な挙動を抑止し、そして滑らかかつソフトな着座動作が助長され、前記と同様の効果が発揮される。 The high-pressure accumulator structure inwardly to the boundary of the inner cylindrical member to form a low-pressure accumulator structure with a ring-shaped piston outward side, one for forming an oil chamber between the piston of each accumulator forming a communication path to an end cover, this be provided 挿凹 portion fitted to the small diameter boss portion and out the excess reaction behavior of the high-pressure piston in the switching point between the high-pressure stage and a low pressure stage arresting, and smooth and soft seating action is promoted, the same effect is exhibited. 加えて、二重配置のアキュムレータとなることから、装置全体の短小化は飛躍的に進む。 In addition, since the accumulator of the double arrangement, shortening of the entire apparatus goes dramatically.

前記小径ボス部に圧油給排路を形成しておけば、小径ボス部が嵌挿凹部から抜け出るとき、および嵌挿凹部に嵌まり込もうとするときの高圧用油室と嵌挿凹部すなわち連通路との間を移行する作動油量を徐々に増減してピストンに負担を及ぼさない加減速度を与え、低圧段階と高圧段階との間の遷移をより一層滑らかにする。 By forming a pressure oil supply and discharge passage to the small-diameter boss, 挿凹 unit fitted with a high-pressure oil chamber when trying Komimo fits in when exiting 挿凹 portion fitting the small diameter boss portion, and the insertion fitting recess portion i.e. giving acceleration which does not adversely burden on the piston gradually increases or decreases the amount of hydraulic oil to migrate between the communicating passage, to further smooth the transition between the low-pressure stage and high pressure stage.

低圧用油室のみが油圧回路に直結され、内筒部材には低圧用油室と高圧用油室との間で作動油を流通させる複数の透孔を設けておき、一方の端部カバーに近接するにつれて小径となるようにしておけば、高圧用ピストンが端部カバー側に位置するとき、両油室間で移行する作動油量を滑らかに増減して、低圧段階と高圧段階との間での遷移を円滑にする。 Only the low-pressure oil chamber is directly connected to the hydraulic circuit, the inner cylindrical member may be provided a plurality of through holes for circulating the hydraulic oil between the low-pressure oil chamber and the high pressure oil chamber, the one end cover if set to be smaller in diameter as close to, when the high-pressure piston is positioned at the end cover side and smoothly increase or decrease the amount of hydraulic oil to migrate between the two oil chambers, between the low pressure stage and high pressure stage to facilitate the transition in. これは、内筒部材を境にして内方側に低圧用のアキュムレータを、外方側に高圧用を配置しても同様である。 This accumulator for low pressure inwardly to the boundary of the inner cylindrical member, the same be arranged for high pressure outward side.

高圧用油室に通じる補助路にチェックバルブを介装させておけば、回路圧急上昇時の初期圧油を高圧用油室に速やかに導入することができる。 If by interposing a check valve in the auxiliary passage leading to the high pressure oil chamber, it can be introduced quickly the initial pressure oil during circuit 圧急 raised to the high pressure oil chamber. 小径ボス部が嵌挿凹部から抜け出る時点での油室の圧力急変がチェックバルブからの送油によって軽減され、油室で発生する衝撃や異音の発生を抑えることができる。 Pressure sudden change in the oil chamber at the time the small-diameter boss comes out of the insertion fitting recess portion is reduced by the oil feed from the check valve, it is possible to suppress the generation of shock and noise generated in the oil chamber.

一方、チェックバルブは油室から連通路へ出ようとする油の流れを阻止するから、回路圧の急降下による作動油の油室抜け量を抑制する。 On the other hand, the check valve from blocking the flow of oil to get away from the oil chamber to the communicating passage, suppressing oil chamber missing amount of hydraulic oil by the dive of the circuit pressure. これによって、小径ボス部が嵌挿凹部に入るときの油の絞り流れの発生は損なわれず、ピストンのソフトな着座を助長して、急停止したなら生じるガスのシール機構抜けが起こらないようにしておくことができる。 Thus, the occurrence of oil flow restriction when entering the 挿凹 portion fitting the small diameter boss portion is not impaired, and promote soft seating of the piston, as occurs if the sudden stop missing sealing mechanism of the gas does not occur it can be placed. ちなみに、小径ボス部が設けられていない場合でも、チェックバルブは急昇圧当初に高圧用油室への送油量を増やして高圧用ピストンの初期動作を補助し、また、降圧時には補助路の遮断で排油終盤におけるピストンの急減速を和らげる。 Incidentally, even when the small-diameter boss portion is not provided, the check valve will assist the initial operation of the high pressure piston to increase the oil feeding amount to the high pressure oil chamber suddenly boosted initially also blocking the auxiliary passage at the time of buck in relieve rapid deceleration of the piston in the oil discharge late.

以下に、本発明に係る二段圧吸収式ピストン型アキュムレータ装置を、その実施の形態を表した図面に基づいて詳細に説明する。 Hereinafter, the two-stage pressure-absorbing piston type accumulator according to the present invention will be described in detail with reference to the drawings showing embodiments thereof. 図1は、油圧回路において圧力の変動した作動油を低圧時と高圧時で異なるばね定数に基づき給排させることができるようにした複合アキュムレータ装置1の一例であり、高圧用アキュムレータ構造2のピストン3と低圧用アキュムレータ構造4のピストン5とが対向する形式となっている。 Figure 1 is an example of a composite accumulator device 1 as a hydraulic oil pressure fluctuations can be discharged sheet on the basis of different spring constants at low pressure at a high pressure in the hydraulic circuit, the high-pressure accumulator structure 2 piston 3 and the piston 5 of the low-pressure accumulator structure 4 is in the form of opposing. このようなアキュムレータによって車載等のための小型化を図ることができるようにするだけでなく、複合アキュムレータ装置で発生しがちな圧力段切り替わり時の好ましからざる挙動を抑え、装置の信頼性を向上して耐用性の高いものとすることができるようにしたものである。 The by such an accumulator not only to be able to reduce the size for the vehicle such as to suppress the undesirable behavior when switching likely to occur pressure stage composite accumulator, to improve the reliability of the apparatus it is obtained to be able to have high durability Te.

図1の(a)を参照して、これは左に高圧用アキュムレータ構造2、右に低圧用アキュムレータ構造4が形成されたものであるが、中間部に配置された仕切部材6に各アキュムレータシェル7,8がねじ接合されることによって一体化されている。 Referring to (a) of FIG. 1, this high-pressure accumulator structure 2 to the left, but in which the low-pressure accumulator structure 4 is formed on the right, the accumulators shell in the partition member 6 disposed in an intermediate portion It is integrated by being 7,8 screw joint. 図の左右端にはガス室側シェルカバー(端部カバー)9,10が螺着され、仕切部材6を挟んだ空間内でピストン3,5を変位させるようにしている。 The right and left ends of FIG screwed gas chamber side shell cover (end cover) 9 and 10, so that to displace the piston 3 and 5 in the space interposing the partition member 6. その仕切部材6は高圧用アキュムレータから見ても低圧用アキュムレータから見ても油室側シェルカバーとして機能すると共に、図示しない油圧回路との連結のための口金としての役目を果たす。 Together with the partition member 6 also functions as an oil chamber side shell cover as viewed from the low pressure accumulator also seen from the high-pressure accumulator serves as a mouthpiece for connection with the hydraulic circuit (not shown).

その仕切部材6を挟んで左右には各アキュムレータの油室11,12が形成されることになるので、仕切部材6には、各油室と外部の油圧回路とを繋ぎ、回路圧の昇降に応じて作動油を給排させる連通路13が形成される。 Since its right and left sides of the partition member 6 so that the oil chamber 11 and 12 of the accumulators are formed, the partition member 6, connecting the hydraulic circuit of the oil chamber and the outside, the lifting of the circuit pressure depending communication passage 13 for supplying and discharging hydraulic oil is formed. その油路は軸方向に延びる高圧用通路13A、低圧用通路13Bと、油圧回路の配管を接続するプラグ孔14で終わる半径方向へ延びた主通路13Cとからなる。 The oil path composed of a high-pressure passage 13A, the low-pressure passage 13B extending in the axial direction, a main passage 13C extending radially ending in a plug hole 14 for connecting the piping of the hydraulic circuit. その仕切部材6とは反対に位置する各シェルカバー9,10にはガスの装入栓15,16があり、これを介してピストン3,5とシェルカバー9,10との間のガス室17,18に初期圧が蓄えられる。 Its the partition member 6 and each shell cover 9 located on the opposite may instrumentation Nyusen 15, 16 of the gas, the gas chamber between the piston 3,5 and the shell cover 9 through which 17 , the initial pressure is stored in 18.

ところで、高圧用ピストン3には、その油室側に小径ボス部19が高圧用通路13Aの開口に向けて突出するように設けられる。 Meanwhile, the high-pressure piston 3, the small diameter boss portion 19 is provided so as to protrude toward the opening of the high-pressure passage 13A on the oil chamber side. 一方、高圧用油室11に臨む通路13Aの開口部にはその小径ボス部19を出入りさせる嵌挿凹部20が形成される。 On the other hand, the opening of the passage 13A facing the high pressure oil chamber 11 挿凹 portion 20 fitted to and out of the small-diameter boss portion 19 is formed. この凹部20は図2の(b)に示すように小径ボス部19が僅かな隙間を残す程度に嵌まり込む内径が与えられ、小径ボス部19の大部分が嵌挿凹部20から抜け出るまでの間は僅かな周囲隙間を通して、油室11(図では油を収容していないため室幅は線でしか表されていない)を徐々に昇圧させ、逆の排油時には、小径ボス部19が嵌挿凹部20に収まりきるまでの間は急激な油抜けを抑制するように作用する。 The recess 20 has an inner diameter that writing fits to the extent that small diameter boss portion 19 leaves a slight gap given as shown in (b) of FIG. 2, to exit the 挿凹 portion 20 fitting the majority of the small-diameter boss portion 19 during the through slight ambient clearance, the oil chamber 11 (chamber width because it does not contain the oil in the drawing is represented only by a line) gradually boosts, during reverse oil drain, fitted small diameter boss 19 until as possible fits 挿凹 unit 20 acts to suppress the rapid oil loss.

その嵌挿凹部20の周縁部には高圧用ピストン3の油室側外縁部3aを当接させる止め座面21が形成され、油圧回路から及ぶ圧力がガス室17の封入圧より低い場合には高圧用油室11に原則として油溜まりを生じさせないようにしている。 The peripheral portion of the insertion fitting recess portion 20 clamp seating surface 21 for abutting the oil chamber side edge portion 3a of the high-pressure piston 3 is formed, if the pressure ranging from the hydraulic circuit is lower than the filling pressure of the gas chamber 17 so that without causing the oil reservoir in principle to the high pressure oil chamber 11. 嵌挿凹部20が浅くて小径ボス部19の先端が底当たりするなどの場合には(図示せず)、油室11の残油が次回の高圧油到達によるピストン変位時に負圧を生じさせ、ピストンの動き始めの滑らかさを阻害することになるからである。 If the tip of the small-diameter boss portion 19 挿凹 portion 20 is shallow fit is such as per bottom (not shown), the remaining oil in the oil chamber 11 causes a negative pressure when the piston displacement by the next high-pressure oil reached, This is because will inhibit the smoothness of the piston movement beginning.

二段圧対応型のアキュムレータとしての動作を、以下に具体的に述べる。 The operation of the two-stage pressure corresponding type accumulators, specifically described below. 図2の(a)は、ガス室17,18にそれぞれの所定圧を封入した状態にある。 (A) in FIG. 2 is in a state encapsulating predetermined pressure respectively to the gas chamber 17, 18. これを油圧回路に接続して、その回路が通常稼働圧状態で例えば3MPaであるとすると、低圧用ピストン5は2.5MPaで封入されているガスを圧縮して作動油を低圧用油室12に収容しようとする。 Connect it to the hydraulic circuit, when the circuit is assumed to be, for example, 3MPa normal operating pressure conditions, the low-pressure piston 5 is low-pressure oil chamber hydraulic oil to compress the gas sealed in the 2.5 MPa 12 When you try to accommodate to. いま、作動油圧が4.5MPaに上昇すると(b)のようにピストン5は約半行程をストロークする。 Now, stroke approximately half stroke piston 5 as the hydraulic oil pressure rises to 4.5 MPa (b).

引続き上昇して例えば6MPaが作用したとすると、小径ボス部19の前面にその圧力が作用すると共に、図1の(a)に示すように小径ボス部19と嵌挿凹部20との間の僅かな隙間を通して、矢印22のごとく作動油が油室11に入る。 Continuing with rises and example 6MPa is to applied, with acts the pressure in front of the small-diameter boss portion 19, just between the 挿凹 portion 20 fitting a small-diameter boss portion 19 as shown in FIG. 1 (a) through a gap, the hydraulic oil as indicated by arrow 22 enters the oil chamber 11. 油室に急激に高圧油が入るわけではないので、ピストン3は徐々に後退を始める。 Since not abruptly high pressure oil enters the oil chamber, the piston 3 gradually begin to retract.

小径ボス部19が図1の(b)のように嵌挿凹部20から完全に抜け出ると、高圧用ピストン3は図3の(a)に示すように、その両面に作用する圧力が均衡するところまで後退する。 When the small-diameter boss portion 19 comes out completely from 挿凹 portion 20 fitted as shown in Figure 1 (b), the high-pressure piston 3, as shown in FIG. 3 (a), where the pressure acting on both sides are balanced until the recession. このように、ピストン3の動きが高圧油の作用に即応して敏感に動作することは抑えられ、ピストンの急変位によるガスの噛み込み、またはピストンによる高圧油塞き止め作用によるシール負担の増大といった問題が解消される。 Thus, it is suppressed that the movement of the piston 3 operates sensitively with responsiveness to the action of high pressure oil, biting of the gas due to sudden change position of the piston, or piston increases the seal borne by the high-pressure oil blocked action by a problem can be solved.

一時的な昇圧で6MPaとなっていた高圧用アキュムレータ2から作動油が引くと、図1の(b)を経て(a)に戻る。 When the temporary hydraulic oil draws from the high-pressure accumulator 2, which has been a 6MPa the booster returns to the through of FIG. 1 (b) (a). 小径ボス部19が嵌挿凹部20に嵌入し始めると油室11の油の急激な抜けは抑えられ、ピストン3は仕切部材6に衝撃を伴うことなくソフトに着座する。 When the small-diameter boss portion 19 begins to fit into the insertion fitting recess portion 20 of the oil chamber 11 oil sudden dislodgement is suppressed, the piston 3 is seated on soft without shock in the partition member 6. 以後油圧回路が5MPa未満で変動すれば低圧用アキュムレータ4による圧油給排作用を、5MPaを超えて変動すれば高圧用アキュムレータ2も加えた圧油給排作用がなされる。 The pressurized oil supply and discharge action of the low-pressure accumulator 4 if subsequent hydraulic circuit varies less than 5 MPa, the high-pressure accumulator 2 also pressure oil supply and discharge action plus is made if vary more than 5 MPa.

ところで、低圧段階から高圧段階への切り替わりもしくはその逆の切り替わりが繰り返されるような小刻みな昇圧があったとしても、上記した高圧用ピストンの着座・離座の低加速度化は、高圧用ピストン3の過敏な挙動を抑える。 Incidentally, even if wiggling booster as switches from the low pressure stage to the high pressure stage or the switching of the reverse is repeated, lower acceleration of the seat-away seat of the high-pressure piston that described above, the high-pressure piston 3 keep the sensitive behavior. 従って、高圧用ピストン3が図2の(b)のごときホームポジションにあっても、チャタリングをひき起こすことは可及的に少なくなる。 Therefore, the high-pressure piston 3 even in the home position, such as in FIG. 2 (b), it causes a chattering is reduced as much as possible. このようなことから、作動油圧の大きさを二段階に分けて圧油収容量を変更し、油圧回路における低圧段階および高圧段階それぞれにおける昇圧を、異なるばね定数のアキュムレータによって軽減するに際しての問題が解決される。 For this reason, the size of the hydraulic pressure to change the pressure oil storage amount in two steps, a step-up in each of the low-pressure stage and high pressure stage in the hydraulic circuit, the problem of when to reduce the accumulator different spring constants It is solved. 仕切部材6は二つのアキュムレータのシェルカバーともなるから装置を短くし、車両のサスペンション機構用などとしての小型化の要望にも応えられるものとなる。 The partition member 6 is shorter device from also a shell cover of the two accumulators, also intended to meet the demand for miniaturization of the like for a suspension mechanism of a vehicle.

上記した小径ボス部19の周面先端部に丸みを与えておけば(図示せず)嵌挿凹部20への進入時の小競りを回避できることは言うまでもないが、図2のいずれからも分かるように、その部分を截頭円錐面とすることによって、嵌挿凹部20の内壁との間に断面くさび形の環状路23を形成しておく。 It goes without saying that avoids small bid upon entry into Shumen if giving rounded tip (not shown) the insertion fitting recess portion 20 of the small-diameter boss portion 19 described above, as can be seen from any of the figures 2 to, by that part and frusto-conical surface, should form a cross-section wedge-shaped annular channel 23 between the inner wall of the insertion fitting recess portion 20. この環状路は上記した小競りを解消するだけでなく、図1の(a)の状態にあるとき、すなわち小径ボス部19が嵌挿凹部20から完全に抜け出す直前での作動油の油室11への流入量を漸増させ、ピストンの加速度を滑らかに増加するように作用する。 This annular passage is not only to eliminate the small bid as described above, when in the state of FIG. 1 (a), i.e., the oil chamber of the hydraulic oil immediately before the escape completely from 挿凹 portion 20 fitting the small diameter boss 19 11 increased gradually the inflow into, acts to smoothly increase the acceleration of the piston. 逆の動きのときには、油室11から嵌挿凹部20への移行を徐々に規制して、ピストンの減速度を滑らかに変化させる。 When the reverse movement, the shift to 挿凹 portion 20 fitted from the oil chamber 11 gradually restricted, smoothly changing the deceleration of the piston.

図3の(b)は、仕切部材6に連通路13の途中から高圧用油室11に直接通じる補助路24を設け、これに油室方向への流れのみを許容するチェックバルブ25を介装させた例である。 (B) in FIG. 3, interposed a check valve 25 which an auxiliary passage 24 which leads directly to the high pressure oil chamber 11 in the partition member 6 from the middle of the communication passage 13, which to permit flow only in the oil chamber direction it is an example that was. これによれば、高圧段階に入った時点で連通路13中の圧油がチェックバルブ25をも経て油室11に導かれる。 According to this, the pressure oil in the communicating path 13 upon entering the high pressure stage is introduced into the oil chamber 11 also through the check valve 25. ピストン3の油室側に浅い円周溝3bでも形成しておけば、その圧力をピストンに作用させやすくなる。 By forming any shallow circumferential groove 3b to the oil chamber side of the piston 3, it tends to exert their pressure on the piston. このようにして補助路24を介して油圧急上昇時の初期圧油を高圧用油室11に先送りしておけば、昇圧幅が大きいがために小径ボス部19が嵌挿凹部20から短時間のうちに抜け出るようなことになっても、油室11における圧力の大きい急変は抑えられ、小径ボス部の抜けによるショックや異音の発生が防止される。 In this way Oke put off the initial pressure oil at the hydraulic jump through the auxiliary passage 24 to the high pressure oil chamber 11, boost width is large but the small diameter boss portion 19 is fitted from 挿凹 portion 20 of the short time for even if the exit such that the inner, sudden changes greater the pressure in the oil chamber 11 is suppressed, the occurrence of shock and abnormal noise due to omission of the small-diameter boss portion is prevented.

逆に、高圧用油室11から高圧油が急激に油圧回路へ戻される場合、チェックバルブ25は油室11から補助路24を経て連通路13に出ようとする流れを阻止する。 Conversely, if the high-pressure oil from the high pressure oil chamber 11 is returned to the rapid hydraulic circuit, the check valve 25 prevents a flow to get away to the communication passage 13 through the auxiliary passage 24 from the oil chamber 11. これは、油圧回路の圧力急降下によるピストン3の戻り時の作動油の抜け速度や排油量の増大化を抑え、小径ボス部19が嵌挿凹部20に入るときの油の絞り流れの発生を損なわせず、高圧用ピストン3のソフトなリターンを保証する。 This suppresses the increase in the dropout rate and discharge oil amount of the hydraulic fluid during the return of the piston 3 by the pressure descent of the hydraulic circuit, the occurrence of oil flow restriction when the small-diameter boss 19 enters the insertion fitting recess portion 20 without compromising ensures soft return of the high pressure piston 3. ピストンの急停止に伴うガスのシール機構抜け、すなわちガスが油室に進入するといったことはなくなる。 Omission sealing mechanism of the gas due to the sudden stop of the piston, i.e. will not be such gas enters the oil chamber.

上記した例はいずれも仕切部材6に各アキュムレータ構造のためのシェル7,8を螺着させたものであるが、図4の(a)のように、一つのシリンダ状シェル8Aに仕切部材6Aを内装させ、それを境に二つのアキュムレータ構造2,4を形成することもできる。 Examples described above is obtained by screwing the shell 7,8 for each accumulator structure both the partition member 6. However, as in FIG. 4 (a), the partition member 6A in a cylindrical shell 8A was furnished, it is also possible to form two accumulator structure 2,4 it as a boundary. また、(b)などのように、低圧用ピストン5Aに小径ボス部19Aを形成しておいてもよい。 Also, it may be formed a small-diameter boss portion 19A, in the low-pressure piston 5A such as (b). 低圧用アキュムレータにおける小径ボス部の作用は特に期待するところでないが、シェルの外観が左右酷似することにより逆据え付けとなっても、位置的に都合のよい方を高圧用アキュムレータとして機能させることができる。 Although not a place particularly expected effects of the small-diameter boss portion in the low-pressure accumulator, even when a reverse mounting by the appearance of the shell left very similar, it can function positionally towards convenient as the high-pressure accumulator .

この例には、上記した環状路23に代わる凹み路26が設けられている。 Examples include recessed passage 26 in place of the annular passage 23 mentioned above is provided. これは、小径ボス部19の先端周面部に位置して軸方向へ延びるもので、ピストン3に施されたような先端になるほど幅および深さが大きくなる適数個のノッチ26aであったり、ピストン5Aに描かれたごとくに幅および深さが一定の溝26bであったりする。 This is intended to extend in the axial direction and located at the tip peripheral surface of the small-diameter boss portion 19, or a suitable several notches 26a that as the width and depth will tip as applied to piston 3 is increased, width and depth as depicted in the piston 5A is or a constant groove 26b. いずれにしても、環状路23と同じ作用をしてその目的を果たす。 In any case, it serves its purpose by the same action as the annular passage 23.

図5の(a)は、小径ボス部19の内部を経て外周面に至る導孔路27を設けた例であり、(b)のように導孔路27Aの出口もしくは入口に所望する大きさの小孔28aを備えたプラグ28A,28Bを取り付けることもできる。 (A) of FIG. 5 is an example in which a Shirubeanaro 27 extending to the outer peripheral surface through the inside of the small-diameter boss portion 19, sized to desired at the outlet or inlet of Shirubeanaro 27A as (b) plug 28A, can be attached and 28B having a small hole 28a of the. 小孔28aの径選定によって圧力段の切り替わり時の繋ぎ特性を変えることができ、ピストンの標準化も進めやすくなる。 Can change the connecting characteristics when switching of the pressure stage by size selection of the small holes 28a, the standardization of the piston also easily proceed. 環状路23を始め凹み路26、導孔路27といったこれらの圧油給排路は、小径ボス部が嵌挿凹部に進入したり退出するときの高圧用油室と連通路との間を移行する作動油量を徐々に増減してピストンに負担を及ぼさない加減速度を与えるなど、低圧段階と高圧段階との間の遷移をより一層滑らかにする。 Recessed passage 26 start an annular passage 23, these pressure oil supply drainage path such Shirubeanaro 27, transition between the high pressure oil chamber and the communication path when exiting or entering the 挿凹 portion fitting the small diameter boss such as providing the acceleration that does not adversely burden on the piston gradually increases or decreases the amount of hydraulic oil to be even more smooth the transition between the low-pressure stage and high pressure stage.

図6、図7(a)および(b)等の例は、アキュムレータシェルを二重筒としたものである。 6, like FIGS. 7 (a) and (b), the accumulator shell is obtained by the double cylinder. これは、小径ボス部19と嵌挿凹部20を設ける点(図6を参照)、チェックバルブ25(図7の(a)を参照)、圧油給排路23(図6を参照),26(図7の(b)を参照),27(図8の(a)を参照)やプラグ28(図8の(b)を参照)などを設けてもよい点については先の例と変わりがないが、二重筒を採用するゆえの相違が以下に述べるごとく存在する。 This is the point of providing a 挿凹 portion 20 fitting a small-diameter boss portion 19 (see FIG. 6), (see FIG. 7 (a)) the check valve 25, pressure oil supply and discharge passage 23 (see FIG. 6), 26 (see (b) in FIG. 7), 27 for that may be the like provided (FIG see (a) of 8) and the plug 28 (see FIG. 8 (b)) is the same as the previous example no, but differences because adopting a double cylinder is present as described below.

まず、図6に示すように、高圧用アキュムレータ構造2Aが内筒部材31の内方側に、低圧用アキュムレータ構造4Aが外方側に形成され、後者のピストン5Bは前者のピストン3と異なりリング状となっている。 First, as shown in FIG. 6, the inner side of the inner cylindrical member 31 is a high pressure accumulator structure 2A, the low-pressure accumulator structure 4A is formed on the outer side, the latter piston 5B is different from the former piston 3 ring It has become a Jo. シェルの端部カバー32,33は内筒部材31と外筒部材34とを同心状に保持し、一方の端部カバー32はピストン3,5Bと共にそれぞれの油室11A,12Aを画成し、他方の端部カバー33はガス室17A,18Aを画成する。 End cover 32, 33 of the shell holds the inner cylindrical member 31 and the outer cylindrical member 34 concentrically, one end cover 32 defines each of the oil chambers 11A, the 12A together with the piston 3,5B, the other end cover 33 defines a gas chamber 17A, the 18A. 前者には連通路35が、後者にはガスを充填する装入栓15A,16Aが取り付けられる。 Communicating passage 35 in the former, the latter in the instrumentation Nyusen 15A for filling the gas, 16A is attached.

このような二重筒アキュムレータ装置1Aにおいても、高圧段階と低圧段階との間の切り替わり目における高圧用ピストン3の過剰反応的な挙動を抑え、滑らかな加減速変化による変位挙動やソフトな着座動作が助長される。 In such a double cylinder accumulator 1A, overreaction behavior suppressed, displacement behavior and soft due to smooth acceleration and deceleration changes the seating operation of the high-pressure piston 3 in the switching point between the high-pressure stage and a low pressure stage There is promoted. サイズ的な面では、二重配置による装置全体の短小化は当然のこととは言え目を見張る。 The size of view, striking said to be shortening of the entire apparatus according to the double arrangement granted. アキュムレータ二基分の圧油収容能力を確保しても、その直径方向の嵩張りの増加は思いのほか小さく抑えられることは計算するまでもない。 Be reserved accumulator second base component of the pressure oil capacity, the increase in the bulk of the diameter direction needless to compute be suppressed surprisingly small.

図9は上で述べた小径ボス部19や嵌挿凹部20を設けず、複数の連通小孔を内筒部材31に設け、これによって、両油室間で移行する作動油量を滑らかに増減し、低圧段階と高圧段階との切り替わり時のピストン挙動を安定させることができるようにしたものである。 9 without providing the small-diameter boss portion 19 and the insertion fitting recess portion 20 mentioned above, a plurality of small communication holes in the inner cylindrical member 31, thereby smoothly increase or decrease the amount of hydraulic oil to migrate between the two oil chambers and is obtained by such a piston behavior when switching between the low-pressure stage and high pressure stage can be stabilized. 詳しく述べれば、一方の端部カバー32に形成される連通路36は、(a)に示すように、外部の油圧回路と低圧用油室12Aとのみを繋ぎ、油圧回路の上昇があると作動油を低圧用油室経由で高圧用油室に導くようにしている。 Stated specifically, actuating the communication passage 36 formed in one end cover 32 includes a (a), the connecting only an external hydraulic circuit and the low-pressure oil chamber 12A, there is a rise in the hydraulic circuit oil and to guide the high pressure oil chamber via the low-pressure oil chamber.

内筒部材31には、図9の(b)に示すように、低圧用油室12Aと高圧用油室11Aとの間で作動油を流通させる直径の異なる透孔37が一方の端部カバー32の近傍に設けられている。 The inner cylindrical member 31, as shown in (b) of FIG. 9, the oil chamber 12A and the one end cover different holes 37 of diameters for circulating the hydraulic oil between the high pressure oil chamber 11A for the low pressure It is provided in the 32 vicinity of. それらの透孔は、高圧用ピストン3Aが一方の端部カバー近くで変位するとき、両油室間で移行する作動油量を滑らかに増減させるべく、端部カバー32に近接するにつれて孔径が小さくなるように与えられている。 These holes when the high pressure piston 3A is displaced near one end cover, in order to smoothly increase or decrease the amount of hydraulic oil to migrate between the two oil chambers, pore size smaller as close to the end cover 32 They are given so that. なお、低圧用ピストン5Cはリング部の一断面における輪郭が後述する図11のように矩形であってもよいが、この例では低圧用油室側の内方部位に空隙5cを確保して、低圧用ピストンの内周シール機構38が透孔列と干渉することがないように配慮されている。 Incidentally, the low-pressure piston 5C may be rectangular as shown in FIG. 11, the contour of a section of the ring portion will be described later, in this example to ensure voids 5c inward site of the low-pressure oil chamber side, inner circumferential sealing mechanism 38 of the low pressure piston is consideration so as not to interfere with the through hole row.

連通路36からの圧油は低圧用アキュムレータ構造で昇圧緩衝がなされるが、高圧段階に入ると低圧用油室12Aを経て透孔37から高圧用油室11Aに入る。 Pressure oil from the communication passage 36 is boosted buffered with a low pressure accumulator structure is made, entering the high pressure oil chamber 11A from the through hole 37 via the low-pressure oil chamber 12A enters the high pressure stage. 高圧用ピストン3Aは図9の(a)のようにホームポジションにあるが、第一の透孔37aから僅かな圧油が高圧用油室に導入される。 High pressure piston 3A is in the home position as shown in (a) of FIG. 9, a slight pressure oil from the first through hole 37a is introduced into the high pressure oil chamber. ピストンが変位し始めると、(b)に示した第二の透孔37bが開口することになり、導入油量が増える。 When the piston begins to displace, it will be opening a second hole 37b shown (b), the introduction amount of oil is increased. さらに第三の透孔37cも開口すれば、この三つの透孔から進入する圧油を受け入れることになる。 In more even opening the third hole 37c, it will accept the pressurized oil entering from the three holes. 透孔の開口面積は三段階に分けて大きくなるから、流入油量は次第に急増加する。 Since the opening area of ​​the through hole is larger divided into three stages, the inflow oil quantity abruptly increases gradually. この例では、高圧用ピストン3Aが透孔37を開閉する「滑りスプール」としても機能していることが分かる。 In this example, it can be seen that high pressure piston 3A is functioning as a "slip spool" for opening and closing the through hole 37.

このようなアキュムレータ装置においては小径ボス部がないから、それに形成される圧油給排路も存在しないが、上記したごとく周方向には散らばるが軸方向には列をなすように配置された透孔列がそれに類する作用を実現し、高圧用ピストンの挙動もほぼ同様となる。 Because there is no small-diameter boss portion in such accumulator device, permeable but not present pressure oil supply and discharge passage formed thereto, scattered in the circumferential direction as described above but which are arranged to form a row in the axial direction realized the effect of hole arrays is similar to that, the behavior of the high-pressure piston is also substantially the same. ちなみに、図10の(a)に示したようにチェックバルブ25を連通路36と高圧用油室11Aに通じる補助路24に介装しておくこともでき、それによる給排補助作用も先に説明したところと異なるところはない。 Incidentally, you can leave interposed auxiliary passage 24 communicating the check valve 25 as shown in (a) of FIG. 10 in the communication passage 36 and the high pressure oil chamber 11A, the supply and discharge auxiliary act earlier by it there is no place as different from that described. (b)は高圧用ピストン3Bのストロークエンドを第一透孔37aを超えて端部カバー32に寄せた例である。 (B) shows an example in which asked the stroke end of the high pressure piston 3B First hole 37a to beyond the end cover 32. 作用として特段の違いが生じるものでないが、ピストンの異なる変形例を教えている。 Not intended particular difference occurs as a function, but teaches another modification of the piston.

図11は内筒部材31を境にして形成されるアキュムレータの低圧用および高圧用を逆にした例である。 Figure 11 is an example in which the low pressure and for high pressure accumulator formed by an inner tubular member 31 as a boundary to the reverse. 連通路39は一直線となっているが、低圧用油室12Bのみに通じている点で前例と変わりはない。 Although the communication passage 39 has a straight line, no difference with the precedent in that leads only to the low-pressure oil chamber 12B. 低圧用ピストン5Dの外周シール機構40が透孔37と擦れないように変形されているのも、図9と同じ思想である。 Also the peripheral seal mechanism 40 of the low pressure piston 5D is deformed so as not rubbed with holes 37, the same concept as in FIG. 高圧用ピストン3Cが(a)から(b)に変位する間に透孔37a,37b,37cを次々と開いて流通量を増やすことも、先の説明と変わらない。 Hole 37a while the high pressure piston 3C is displaced (a) from (b), 37b, also to increase the circulation amount 37c opened one after another, not different from the preceding description.

図12は、チェックバルブ25を設けた例である。 Figure 12 is an example in which a check valve 25. 補助路24Aの形は図7などとは少し異なるが、高圧用油室11Bに流す点で機能的に同じである。 Shape of the auxiliary passage 24A is slightly different although the like 7, which is functionally the same in that flow to the high pressure oil chamber 11B. それゆえ、低圧用油室12Bから出る補助路24Bにチェックバルブルブ25Aを介装することもできる。 Therefore, it is also possible to interposed a check valve Lube 25A in the auxiliary passage 24B exiting from the low-pressure oil chamber 12B. これらの例におけるチェックバルブは圧油の導入促進と、導出抑制機能を発揮するから、高圧用ピストンの加減速調整に寄与することは先に述べたことと特に異ならない。 Check valve and promoting the introduction of the pressurized oil in these examples, because exhibits emission suppressing function, not particularly different from that previously described is to contribute to the acceleration and deceleration adjustment of the high pressure piston.

本発明は以上の説明から分かるように、低圧用アキュムレータと高圧用アキュムレータに作動油圧の大きさを二段階に分けて収容させ、油圧回路における低圧段階および高圧段階それぞれにおける一時的な昇圧を異なるばね定数のアキュムレータによって緩衝させることができる。 The present invention, as understood from the above description, the size of the hydraulic pressure to the low-pressure accumulator and the high-pressure accumulator is accommodated in two stages, different spring temporary boost in each low-pressure stage and high pressure stage in the hydraulic circuit it can be buffered by the accumulator constant. そして、複合アキュムレータとしての装置の長さや嵩を減らして小型化を図ることにできるようになったが、一体化させるゆえに遭遇するピストンの不安定な挙動も解消され、極めて実用性の高い複合アキュムレータとすることができる。 Then, it became to be able to be miniaturized by reducing the length and bulk of the device as a composite accumulator, unstable behavior of the piston encountered because of integrating also be eliminated, extremely high practicality composite accumulator it can be.

本発明に係る二段圧吸収式ピストン型アキュムレータ装置の構成断面図。 Configuration sectional view of a two-stage pressure-absorbing piston type accumulator according to the present invention. 油圧回路接続前の状態および低圧段階での圧油収容状態を示す動作図。 Operation view illustrating a pressurized oil accommodating state in the hydraulic circuit connecting the previous state and the low-pressure stage. 高圧段階での圧油収容状態を示す動作図およびチェックバルブ介装図。 Operation view illustrating a pressurized oil accommodating state in the high-pressure stage and check valves KaiSozu. 異なる例の断面図。 Sectional views of different examples. さらに異なる例の断面図。 Sectional view of still another example. 二重シェルによる複合アキュムレータ装置の断面図。 Sectional view of a composite accumulator according double shell. 二重シェル型アキュムレータの変形例。 Modification of the double shell type accumulator. 二重シェル型アキュムレータの異なる変形例。 Different variants of the double shell type accumulator. 内筒部材に透孔を備えさせた二重シェル型アキュムレータの断面図。 Sectional view of a double shell type accumulator which gave comprising a hole in the inner cylindrical member. 透孔を備える複合アキュムレータの変形例。 Modification of a composite accumulator with a through hole. 高圧用アキュムレータ構造を内筒部材の外方に配置した断面図。 Sectional view is arranged outside the inner cylindrical member and high-pressure accumulator structure. 内筒部材の外方に高圧用アキュムレータ構造を設けた変形例。 Modification in which a high-pressure accumulator structure outwardly of the inner cylindrical member. 従来技術としての複圧吸収可能なアキュムレータ装置の構成図。 Block diagram of multi-pressure absorbable accumulator apparatus as the prior art. 高圧段階に入った作動説明図。 Operation illustration entering the high pressure stage.

符号の説明 DESCRIPTION OF SYMBOLS

1,1A…複合アキュムレータ装置、2,2A…高圧用アキュムレータ構造、3,3A,3B,3C…高圧用ピストン、4,4A…低圧用アキュムレータ構造、5,5A,5B,5C,5D…低圧用ピストン、6,6A…仕切部材、9,10…ガス室側シェルカバー、11,11A,11B…高圧用油室、12,12A,12B…低圧用油室、13…連通路、17,17A…高圧用ガス室、18,18A…低圧用ガス室、19,19A…小径ボス部、20…嵌挿凹部、23…環状路(圧油給排路)、24,24A,24B…補助路、25,25A…チェックバルブ、26…凹み路(圧油給排路)、27,27A…導孔路(圧油給排路)、31…内筒部材、32,33…シェルカバー(端部カバー)、34…外筒部材、35,36…連通路、3 1, 1A ... complex accumulator, 2, 2A ... high-pressure accumulator structure, 3,3A, 3B, 3C ... high-pressure piston, 4, 4A ... accumulator structure for low pressure, 5,5A, 5B, 5C, 5D ... low pressure pistons, 6, 6A ... partition member, 9, 10 ... gas chamber side shell cover, 11, 11A, 11B ... high-pressure oil chamber, 12, 12A, 12B ... low pressure oil chamber, 13 ... communicating passage, 17 and 17A ... high pressure gas chamber, 18, 18A ... low pressure gas chamber, 19, 19A ... small-diameter boss portion, 20 ... insertion fitting recess portion 23: annular passage (pressure oil supply and discharge passage), 24, 24A, 24B ... auxiliary passage, 25 , 25A ... check valve, 26 ... recessed channel (pressure oil supply and discharge passage), 27, 27A ... Shirubeanaro (pressure oil supply and discharge passage), 31 ... inner cylindrical member, 32, 33 ... shell cover (end cover) , 34 ... outer cylindrical member, 35, 36 ... communicating passage, 3 …透孔、37a…第一の透孔、37b…第二の透孔、37c…第三の透孔、39…連通路。 ... through hole, 37a ... first through hole, 37b ... second through hole, 37c ... third hole, 39 ... communicating passage.

Claims (6)

  1. 油圧回路に発生した一時的な圧力上昇を吸収するため、作動油圧の大きさを二段階に分けて収容量を変更し、油圧回路における低圧段階および高圧段階それぞれにおける昇圧を軽減できるようにした複圧吸収可能なアキュムレータにおいて、 To absorb transient pressure increase that occurred in the hydraulic circuit, the magnitude of the hydraulic pressure to change the storage capacity in two steps, and so can reduce the boost in each low-pressure stage and high pressure stage in the hydraulic circuit double in the pressure it can be absorbed by the accumulator,
    仕切部材を境にして一方の側に高圧用アキュムレータ構造が、他方の側に低圧用アキュムレータ構造が形成され、 High-pressure accumulator structure on one side by the partition member as a boundary, the low-pressure accumulator structure on the other side is formed,
    各アキュムレータ構造のピストンと前記仕切部材との間に油室を、ピストンとアキュムレータシェルの各端部カバーとの間にガス室を画成させ、 The oil chamber between the piston and the partition member of the accumulators structure causes defined a gas chamber between the end cover of the piston and the accumulator shell,
    前記仕切部材には、各油室と外部の油圧回路とを繋ぎ、回路圧の昇降に応じて作動油を給排させる連通路が形成され、 Wherein the partition member, connecting the hydraulic circuit of the oil chamber and the external communication passage for supplying and discharging the hydraulic oil in response to the lifting of the circuit pressure is formed,
    高圧用ピストンの油室側には、小径ボス部が前記連通路の開口に向けて突出して形成され、 The oil chamber side of the high-pressure piston, the small diameter boss portion is formed to project toward the opening of the communication passage,
    高圧用油室に臨む連通路の開口部には前記小径ボス部を出入りさせる嵌挿凹部が設けられ、低圧段階と高圧段階との切り替わり時の高圧用ピストンを滑らかにまた安定して挙動させることができるようにしたことを特徴とする二段圧吸収式ピストン型アキュムレータ装置。 The opening of the communication passage facing the high pressure oil chamber is the insertion fitting recess portion is provided to and out of the small-diameter boss portion, thereby smoothly or stable behavior of the high-pressure piston when switching between the low-pressure stage and high pressure stage two-stage pressure, characterized in that has to be able to absorb piston type accumulator.
  2. 油圧回路に発生した一時的な圧力上昇を吸収するため、作動油圧の大きさを二段階に分けて収容量を変更し、油圧回路における低圧段階および高圧段階それぞれにおける昇圧を軽減できるようにした複圧吸収可能なアキュムレータにおいて、 To absorb transient pressure increase that occurred in the hydraulic circuit, the magnitude of the hydraulic pressure to change the storage capacity in two steps, and so can reduce the boost in each low-pressure stage and high pressure stage in the hydraulic circuit double in the pressure it can be absorbed by the accumulator,
    内筒部材を境にして内方側に高圧用アキュムレータ構造が、外方側にリング状ピストンを備えた低圧用アキュムレータ構造が形成され、 High-pressure accumulator structure inwardly to the inner cylindrical member as a boundary, the low-pressure accumulator structure with a ring-shaped piston outward side is formed,
    内筒部材と外筒部材を同心状に保持する一方の端部カバーと各アキュムレータ構造のピストンとの間に油室を、他方の端部カバーとピストンとの間にガス室を画成させ、 The oil chamber between the one end cover for holding the inner cylindrical member and the outer tubular member concentrically with the piston of each accumulator structure, not defined a gas chamber between the other end cover and the piston,
    一方の端部カバーには、各油室と外部の油圧回路とを繋ぎ、回路圧の昇降に応じて作動油を給排させる連通路が形成され、 On one end cover, connecting the hydraulic circuit of the oil chamber and the external communication passage for supplying and discharging the hydraulic oil in response to the lifting of the circuit pressure is formed,
    高圧用ピストンの油室側には、小径ボス部が前記連通路の開口に向けて突出して形成され、 The oil chamber side of the high-pressure piston, the small diameter boss portion is formed to project toward the opening of the communication passage,
    高圧用油室に臨む連通路の開口部には前記小径ボス部を出入りさせる嵌挿凹部が設けられ、低圧段階と高圧段階との切り替わり時の高圧用ピストンを滑らかにまた安定して挙動させることができるようにしたことを特徴とする二段圧吸収式ピストン型アキュムレータ装置。 The opening of the communication passage facing the high pressure oil chamber is the insertion fitting recess portion is provided to and out of the small-diameter boss portion, thereby smoothly or stable behavior of the high-pressure piston when switching between the low-pressure stage and high pressure stage two-stage pressure, characterized in that has to be able to absorb piston type accumulator.
  3. 前記小径ボス部には、嵌挿凹部を出入りするとき前記連通路と高圧用油室との間を移行する作動油量の増減を補助し、低圧段階から高圧段階へおよびその逆への遷移における高圧用ピストンの動きをより一層滑らかにするための圧油給排路が形成されていることを特徴とする請求項1または請求項2に記載された二段圧吸収式ピストン型アキュムレータ装置。 The said small-diameter boss, in the assist hydraulic oil amount of increase or decrease to migrate between the communicating passage and the high pressure oil chamber, the transition from the low pressure stage to the high pressure stage and vice versa when out of the insertion fitting recess portion It has been two-stage pressure-absorbing piston-type accumulator according to claim 1 or claim 2, characterized in that the pressure oil supply and discharge passage is formed in order to further smooth the movement of the pressure piston.
  4. 油圧回路に発生した一時的な圧力上昇を吸収するため、作動油圧の大きさを二段階に分けて収容量を変更し、油圧回路における低圧段階および高圧段階それぞれにおける昇圧を軽減できるようにした複圧吸収可能なアキュムレータにおいて、 To absorb transient pressure increase that occurred in the hydraulic circuit, the magnitude of the hydraulic pressure to change the storage capacity in two steps, and so can reduce the boost in each low-pressure stage and high pressure stage in the hydraulic circuit double in the pressure it can be absorbed by the accumulator,
    内筒部材を境にして内方側に高圧用アキュムレータ構造が、外方側にリング状ピストンを備えた低圧用アキュムレータ構造が形成され、 High-pressure accumulator structure inwardly to the inner cylindrical member as a boundary, the low-pressure accumulator structure with a ring-shaped piston outward side is formed,
    内筒部材と外筒部材を同心状に保持する一方の端部カバーと各アキュムレータのピストンとの間に油室を、他方の端部カバーとピストンとの間にガス室を画成させ、 The oil chamber between the inner cylindrical member and the outer tubular member and the first end cover for holding concentrically with the piston of the accumulators, not defined a gas chamber between the other end cover and the piston,
    一方の端部カバーには、低圧用油室と外部の油圧回路とを繋ぎ、回路圧の昇降に応じて作動油を給排させる連通路が形成され、 On one end cover, connecting the hydraulic circuit of the low-pressure oil chamber and the external communication passage for supplying and discharging the hydraulic oil in response to the lifting of the circuit pressure is formed,
    前記内筒部材には、低圧用油室と高圧用油室との間で作動油を流通させる直径の異なる透孔が前記一方の端部カバーの近傍に設けられ、 The said inner tube member and a diameter different holes for circulating the hydraulic oil between the low-pressure oil chamber and the high pressure oil chamber provided in the vicinity of the end cover of the one,
    該透孔は、高圧用ピストンが一方の端部カバー近くで変位するとき、両油室間で移行する作動油量を滑らかに増減し、低圧段階と高圧段階との切り替わり時の高圧用ピストンの挙動が安定したものとなるように、前記一方の端部カバーに近接するにつれて孔径が小さく与えられていることを特徴とする二段圧吸収式ピストン型アキュムレータ装置。 The transparent holes, when the high-pressure piston is displaced near one end cover, the amount of hydraulic oil to migrate between the two oil chambers smoothly increase or decrease, the high pressure piston when switching between the low-pressure stage and high pressure stage behavior so becomes stable, the one pore size as close to the end cover, characterized in that the given small bunk pressure absorbing piston type accumulator.
  5. 前記内筒部材を境にして形成されるアキュムレータの低圧用および高圧用を逆にしたことを特徴とする請求項4に記載された二段圧吸収式ピストン型アキュムレータ装置。 Has been two-stage pressure-absorbing piston-type accumulator according to claim 4, characterized in that the low pressure and for high pressure and the reverse accumulator formed by the boundary of the inner cylinder member.
  6. 高圧用油室に通じる補助路を設け、この補助路に油圧急上昇時の初期圧油を高圧用油室に導入するチェックバルブが介装されていることを特徴する請求項1ないし請求項5のいずれか一項に記載された二段圧吸収式ピストン型アキュムレータ装置。 An auxiliary path leading to the high pressure oil chamber, of claims 1 to 5 check valve for introducing the initial pressure oil at a hydraulic jump in the auxiliary passage to the high pressure oil chamber is characterized by being interposed either by two-stage pressure-absorbing piston-type accumulator according to one paragraph.
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