JP2019051925A - Damper device of hydraulic unit of vehicle brake device with damper chamber - Google Patents

Damper device of hydraulic unit of vehicle brake device with damper chamber Download PDF

Info

Publication number
JP2019051925A
JP2019051925A JP2018134248A JP2018134248A JP2019051925A JP 2019051925 A JP2019051925 A JP 2019051925A JP 2018134248 A JP2018134248 A JP 2018134248A JP 2018134248 A JP2018134248 A JP 2018134248A JP 2019051925 A JP2019051925 A JP 2019051925A
Authority
JP
Japan
Prior art keywords
attenuator
throttle
chamber
damping device
action
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.)
Granted
Application number
JP2018134248A
Other languages
Japanese (ja)
Other versions
JP7197299B2 (en
Inventor
ブレンデルファー，ダニエル
Brenndoerfer Daniel
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of JP2019051925A publication Critical patent/JP2019051925A/en
Application granted granted Critical
Publication of JP7197299B2 publication Critical patent/JP7197299B2/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T17/00—Component parts, details, or accessories of power brake systems not covered by groups B60T8/00, B60T13/00 or B60T15/00, or presenting other characteristic features
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
    • B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
    • B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
    • B60T8/40—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition comprising an additional fluid circuit including fluid pressurising means for modifying the pressure of the braking fluid, e.g. including wheel driven pumps for detecting a speed condition, or pumps which are controlled by means independent of the braking system
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
    • B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
    • B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
    • B60T8/40—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition comprising an additional fluid circuit including fluid pressurising means for modifying the pressure of the braking fluid, e.g. including wheel driven pumps for detecting a speed condition, or pumps which are controlled by means independent of the braking system
    • B60T8/4068—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition comprising an additional fluid circuit including fluid pressurising means for modifying the pressure of the braking fluid, e.g. including wheel driven pumps for detecting a speed condition, or pumps which are controlled by means independent of the braking system the additional fluid circuit comprising means for attenuating pressure pulsations
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
    • B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
    • B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
    • B60T8/42—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition having expanding chambers for controlling pressure, i.e. closed systems

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Transportation (AREA)
  • Mechanical Engineering (AREA)
  • Fluid-Damping Devices (AREA)
  • Valves And Accessory Devices For Braking Systems (AREA)
  • Regulating Braking Force (AREA)
  • Sealing Devices (AREA)
  • Diaphragms And Bellows (AREA)

Abstract

To provide a damper device, in particular for a hydraulic unit of a vehicle brake device, with which a resulting power loss can be reduced compared to conventional damper devices.SOLUTION: A damper device 10 of a hydraulic unit of a vehicle brake device is configured with a damper chamber 26 whose chamber volume is variable and with a throttle 36 arranged downstream of the damper chamber 26. According to the invention, the throttle 36 has a variable throttling effect, and this throttling effect is variable as a function of the chamber volume.SELECTED DRAWING: Figure 1

Description

本発明は、室体積が可変である減衰器室と、該減衰器室に後置接続された絞りとを有する、車両ブレーキ装置の液圧ユニットの減衰装置に関する。   The present invention relates to an attenuating device for a hydraulic unit of a vehicle brake device, which includes an attenuator chamber having a variable chamber volume, and a throttle connected downstream of the attenuator chamber.

特に乗用車およびトラックのために使用されるような、液圧式の車両ブレーキ装置においては、車両ブレーキ装置内の圧力脈動およびそれに伴って発生する騒音を避けるために、圧力脈動減衰器が使用される。圧力脈動は、ピストンポンプによってブレーキ液が圧縮される際に発生する。さらに弁の切換時に圧力波が発生する。   In hydraulic vehicle brake devices, particularly those used for passenger cars and trucks, pressure pulsation attenuators are used to avoid pressure pulsations and associated noise in the vehicle brake devices. Pressure pulsation occurs when the brake fluid is compressed by the piston pump. Furthermore, a pressure wave is generated when the valve is switched.

液圧式のブレーキシステムのためのこのような減衰装置は、例えば特許文献１により公知である。ここに記載された圧力脈動減衰器は減衰室を有しており、この減衰室の室体積は、減衰室内に配置されたエラストマーコアが圧力上昇時に圧縮されることにより、変えることができる。減衰室に絞りが後置接続されており、この絞りは絞り孔を有していて、さらにこの絞りにおいて、圧力制限弁が並列接続されてよい。これによって、構成要素を１つにまとめるための許容範囲、および構成要素の機械的な耐負荷能力限度のための許容範囲を超える圧力上昇は避けられるようになる。   Such a damping device for a hydraulic brake system is known, for example, from US Pat. The pressure pulsation attenuator described here has a damping chamber, and the chamber volume of the damping chamber can be changed by compressing the elastomer core disposed in the damping chamber when the pressure rises. A throttle is connected downstream of the damping chamber, the throttle has a throttle hole, and a pressure limiting valve may be connected in parallel in the throttle. This avoids pressure rises that exceed the tolerances for bringing the components together and the tolerances for the mechanical load carrying capacity limits of the components.

しかしながら、ブレーキ液の流れの減衰に伴って、出力損失も発生し、この出力損失は所属のピストンポンプによって補正されなければならない。   However, as the brake fluid flow is attenuated, an output loss also occurs and this output loss must be corrected by the associated piston pump.

独国特許公告第１０３０５３１０号明細書German Patent Publication No. 10305310

本発明の課題は、発生した出力損失を従来の減衰装置と比較して減少させることができる、特に車両ブレーキ装置の液圧ユニットのための減衰装置を提供することである。   The object of the present invention is to provide a damping device, in particular for a hydraulic unit of a vehicle brake device, in which the generated output loss can be reduced compared to a conventional damping device.

本発明によれば、室体積が可変である減衰器室と、この減衰器室に機能的に、若しくは所属の流体の流れ方向で後置接続された絞りとを有する、車両ブレーキ装置の液圧ユニットの減衰装置が提供されている。この絞りは可変な絞り作用を有していて、またこの絞り作用は室体積に依存して可変である。   According to the invention, the hydraulic pressure of a vehicle brake device has an attenuator chamber with a variable chamber volume, and a throttle that is functionally connected to the attenuator chamber or connected downstream in the flow direction of the associated fluid. A unit damping device is provided. This throttling has a variable throttling action, and this throttling action is variable depending on the chamber volume.

この場合、本発明による解決策は、同様に基本的に可変な絞り作用を有する従来の動的な絞りと混同されてはならない。このような絞りの絞り作用は、単に流れてくる流体の流れに依存するだけであって、例えば所属の減衰器室の室体積の大きさに依存することはない。   In this case, the solution according to the invention should not be confused with a conventional dynamic throttle which likewise has a basically variable throttle action. The throttling action of such a throttling simply depends on the flow of the flowing fluid and does not depend on, for example, the size of the chamber volume of the associated attenuator chamber.

従って、高い流れ圧力における動的な絞りは、流れてくる流体の低い流れ圧力におけるよりもやや大きく開放する。この場合、所属の減衰装置の室体積も同時に変化するかどうか、およびどのように変化するかは、絞りのためには重要ではない。動的な絞りのためには、例えば絞りがどのような圧力で流れに晒されるかということだけが重要である。   Thus, the dynamic restriction at high flow pressure opens slightly more than at the low flow pressure of the flowing fluid. In this case, it is not important for the throttling whether and how the chamber volume of the associated damping device also changes. For dynamic throttling, only the pressure at which the throttling is exposed to the flow is important, for example.

これに対して、本発明の解決策は、このような考え方を超えて、絞りの絞り作用を、これが所属の減衰室の室体積の大きさにアクティブに依存して変化するように、変化可能に構成するものである。   In contrast, the solution of the present invention goes beyond this concept and allows the throttling action of the throttling to change so that it changes depending on the size of the chamber volume of the damping chamber to which it belongs. It is composed of

この場合、本発明は、減衰装置の小さい室体積およびひいては大きい減衰作用において、絞り作用は大きくなければならない、という認識に基づいている。これに対して、減衰装置の大きい室体積およびひいては小さい減衰作用において、絞り作用は小さくなければならない。これを構造的に実行するために、本発明による解決策は、可変な出力値としての絞りの絞り作用を、検出しようとする入力値としての室体積に結び付ける。このために特に機械的な装置が設けられており、この機械的な装置によって室体積が検出されるか若しくは算出され、次いで絞り作用が相応にアクティブに変化せしめられる。   In this case, the invention is based on the recognition that the throttling action must be large for the small chamber volume of the damping device and thus for the large damping action. On the other hand, the squeezing action must be small for the large chamber volume and thus the small damping action of the damping device. In order to do this structurally, the solution according to the invention links the throttle action of the throttle as a variable output value to the chamber volume as the input value to be detected. For this purpose, in particular a mechanical device is provided, by which the chamber volume is detected or calculated, and then the squeezing action is correspondingly actively changed.

特に本発明は、最大の大きさの室体積において、減衰装置の減衰作用はいずれにしても完全に失われているという認識に基づいている。この状況において、出力損失を少なくするために、後置接続された絞りの流体の流れの減衰もできるだけ小さくなければならない。この場合、絞り作用は特に同様に完全に失われていなければならない。これは、本発明による解決策によって実現可能である。   In particular, the present invention is based on the recognition that in the largest chamber volume, the damping action of the damping device is completely lost anyway. In this situation, in order to reduce the output loss, the downstream flow restrictor fluid flow attenuation must also be as small as possible. In this case, the squeezing action must in particular be completely lost as well. This can be achieved with the solution according to the invention.

このような理由により、本発明による減衰装置の本発明による発展形態において、絞り作用が室体積の拡大につれて減少され、絞り作用が最大の室体積において概ねゼロに減少されるようになっている。   For this reason, in the inventive development of the damping device according to the invention, the squeezing action is reduced as the chamber volume increases, and the squeezing action is reduced to approximately zero at the maximum chamber volume.

好適には、さらに、減衰器室が変形可能な減衰器ダイヤフラムによって画成されていて、絞りの絞り作用が減衰器ダイヤフラムの変形状態に依存して可変である。選択的に、好適には、減衰器室が位置調節可能な減衰器ピストンによって画成されていて、絞りの絞り作用が減衰器ピストンの調節位置に依存して可変である。２つの発展形態において、絞りの減衰作用は、減衰装置の減衰作用を規定する構成部分の調節位置に直接依存している。依存性は、特にカップリングによって、好適には減衰作用を規定する構成部分および絞り作用を規定する絞りの構成部分の純粋に機械的なカップリングによって形成されている。   Preferably, the attenuator chamber is further defined by a deformable attenuator diaphragm, and the throttling action of the diaphragm is variable depending on the deformation state of the attenuator diaphragm. Optionally, the attenuator chamber is preferably defined by an adjustable attenuator piston, and the throttling action of the throttle is variable depending on the adjustment position of the attenuator piston. In two developments, the damping action of the diaphragm is directly dependent on the adjustment position of the component that defines the damping action of the damping device. The dependence is formed in particular by a coupling, preferably by a purely mechanical coupling of the component defining the damping action and the component of the restriction defining the throttle action.

絞りの絞り作用に影響を及ぼすために、好適には、絞りに対してバイパスが並列接続されており、このバイパスにおいて、絞りの絞り作用を変えるためにバイパス若しくはバイパス開口の大きさが室体積に依存して可変である。この場合、バイパスは、絞り自体の液圧抵抗よりも小さい液圧抵抗を形成する。このような別の液圧抵抗が絞りに対して並列接続で配置されていて、それによって分路を形成することによって、絞りを通ってガイドされた流体路はこの分路によって負荷軽減され得る。液圧的な全抵抗は、減衰装置を通って流れる流体が妨げられることなく流出し、従って絞りの絞り作用が小さくなることによって、低下する。   In order to influence the throttling action of the throttling, preferably a bypass is connected in parallel to the throttling, in which the size of the bypass or bypass opening is changed to the chamber volume in order to change the throttling action of the throttling. It depends on the variable. In this case, the bypass forms a hydraulic resistance that is smaller than the hydraulic resistance of the throttle itself. Such another hydraulic resistance is arranged in parallel with the throttle, thereby forming a shunt, so that the fluid path guided through the throttling can be unloaded by this shunt. The total hydraulic resistance is reduced by the unimpeded flow of fluid flowing through the damping device, and thus by reducing the throttle action of the throttle.

このような形式のバイパス開口は、好適には、バルブシートに対してシールされている弁体によって閉鎖可能である。従って、弁体はバルブシートと共にバイパス開口内で、バイパス開口の液圧抵抗を制御するための制御弁を形成する。   This type of bypass opening is preferably closeable by a valve body that is sealed against the valve seat. Therefore, the valve body forms a control valve for controlling the hydraulic resistance of the bypass opening in the bypass opening together with the valve seat.

この場合、絞りが弁体内に配置されていることによって、特に取り付けスペースを節約すると同時に、機能的に効果的な全体的配置構成が提供され得る。このような弁体内の絞りは、好適には弁体を貫通する絞り開口によって、つまり比較的小さい開口横断面を有する貫通開口によって簡単に形成することができる。弁体はまずバルブシートに当接し、絞りを通過する流体は、オリフィスとして作用する絞り開口だけを通って流れなければならない。減衰装置の室体積が次第に大きくなるにつれて、特に弁体がバルブシートから持ち上げられることによって、バイパスが開放される。絞りを通過する流体は、ほぼ液圧抵抗なしでも、絞りの周囲を流れることができるので、絞り作用は相応に減少される。   In this case, the arrangement of the throttle in the valve body can provide a functionally effective overall arrangement, especially while saving installation space. Such a throttle in the valve body can be formed simply by a throttle opening, preferably through the valve body, i.e. by a through-opening having a relatively small opening cross section. The valve body first abuts the valve seat and the fluid passing through the throttle must flow only through the throttle opening acting as an orifice. As the chamber volume of the damping device gradually increases, the bypass is opened, in particular by lifting the valve body from the valve seat. Since the fluid passing through the restrictor can flow around the restrictor with almost no hydraulic resistance, the constriction action is correspondingly reduced.

特に好適には、弁体は、機械的な連結エレメントによって、室体積に依存して移動可能であり、この場合、連結エレメントは特に減衰器ダイヤフラムまたは減衰器ピストンに連結されている。このような形式の機械的な連結エレメントは、簡単で確実に機能し、かつ同時にコンパクトな、室体積と絞りの絞り作用との間の依存性を得るための構造形を提供する。   Particularly preferably, the valve body can be moved depending on the chamber volume by means of a mechanical connection element, in which case the connection element is connected in particular to an attenuator diaphragm or an attenuator piston. This type of mechanical coupling element provides a structural form for obtaining a dependency between the chamber volume and the throttle action of the restriction, which is simple and reliable and at the same time compact.

この場合、特に好適には減衰器ダイヤフラムまたは減衰器ピストンと弁体との間の連結エレメントは、引張エレメントとして特にタイロッド、牽引ロープまたは牽引パイプとして構成されている。   In this case, the connecting element between the attenuator diaphragm or the attenuator piston and the valve body is particularly preferably configured as a tension element, in particular as a tie rod, traction rope or traction pipe.

本発明による減衰装置の第１実施例の縦断面図である。1 is a longitudinal sectional view of a first embodiment of an attenuation device according to the present invention. 本発明による減衰装置の第２実施例の縦断面図である。It is a longitudinal cross-sectional view of 2nd Example of the damping device by this invention. 本発明による減衰装置の第３実施例の縦断面図である。It is a longitudinal cross-sectional view of the third embodiment of the damping device according to the present invention.

以下に本発明による解決策の実施例を、添付の概略図を用いて詳しく説明する。   In the following, embodiments of the solution according to the present invention will be described in detail with reference to the accompanying schematic drawings.

図１には、車両ブレーキ装置の液圧ユニットの減衰装置１０が示されている。この場合、減衰装置１０は液圧ユニットのハウジング１２に位置しており、この液圧ユニットはここでは、直方体状のブロックとしてアルミニウム材料より形成されている。ハウジング１２から帽子状の減衰器ハウジング１４が突き出している。この場合、ハウジング１２と帽子状の減衰器ハウジング１４の帽子のつば区分との間の接続は、流体密な定置のかしめ加工部１６として構成されている。   FIG. 1 shows a damping device 10 for a hydraulic unit of a vehicle brake device. In this case, the damping device 10 is located in the housing 12 of the hydraulic unit, which is here made of aluminum material as a rectangular parallelepiped block. A cap-shaped attenuator housing 14 protrudes from the housing 12. In this case, the connection between the housing 12 and the cap collar section of the cap-shaped attenuator housing 14 is configured as a fluid-tight stationary caulking section 16.

減衰器ハウジング１４はその内側で円筒形の減衰器内室１８を包囲しており、この減衰器内室１８はさらに、図１に関連して下端部でハウジング１２によって画成されている。減衰器内室１８内に同様に帽子状の減衰器ダイヤフラム２０が位置している。この減衰器ダイヤフラム２０は弾性的な材料より成っていて、その外側に複数の湾曲部２２を備えている。減衰器ダイヤフラム２０は、その下区分がかしめ加工部１６内に組み込まれていて、このような形式によりかしめ加工部１６で定置に保持されている。これによって、減衰器ダイヤフラム２０は、減衰器内室１８を、減衰器ダイヤフラム２０の内部に位置する流体室２４と、減衰器ダイヤフラム２０と減衰器ハウジング１４との間に位置する減衰器室２６とに分離する。減衰器ダイヤフラム２０の変形および運動によって、流体室２４の拡大時に減衰器室２６は縮小し、その逆でもある。   The attenuator housing 14 encloses a cylindrical attenuator chamber 18 on the inside thereof, which is further defined by the housing 12 at the lower end in connection with FIG. Similarly, a hat-shaped attenuator diaphragm 20 is located in the attenuator inner chamber 18. The attenuator diaphragm 20 is made of an elastic material and includes a plurality of curved portions 22 on the outer side thereof. The lower section of the attenuator diaphragm 20 is incorporated in the caulking portion 16 and is held in place by the caulking portion 16 in this manner. Thereby, the attenuator diaphragm 20 includes an attenuator inner chamber 18, a fluid chamber 24 located inside the attenuator diaphragm 20, and an attenuator chamber 26 located between the attenuator diaphragm 20 and the attenuator housing 14. To separate. Due to deformation and movement of the attenuator diaphragm 20, the attenuator chamber 26 shrinks when the fluid chamber 24 expands and vice versa.

供給路２８は、ハウジング１２を貫通して下方から流体室２４内に通じている。この供給路２８を通して、減衰装置１０は、残りの液圧ユニットからブレーキ液を圧力下で供給することができる。   The supply path 28 passes through the housing 12 and communicates with the fluid chamber 24 from below. Through this supply path 28, the damping device 10 can supply brake fluid from the remaining hydraulic units under pressure.

導出路３０が、流体室２４から図１に関連して下方に導き出されている。導出路３０は、流体を減衰装置１０から減衰された形で残りの液圧ユニット内に導出するために用いられる。導出路３０はバルブシート３２によって囲まれており、このバルブシート３２上に、上方から、つまり流体室２４の側から弁体３４が気密に載っている。   A lead-out path 30 is led downward from the fluid chamber 24 in relation to FIG. The lead-out path 30 is used to lead the fluid from the damping device 10 in a attenuated form into the remaining hydraulic unit. The lead-out path 30 is surrounded by a valve seat 32, and the valve element 34 is airtightly mounted on the valve seat 32 from above, that is, from the fluid chamber 24 side.

弁体３４が導出路３０の長手方向で絞り開口３８から挿入されていることによって、弁体３４内に絞り３６が形成されている。絞り開口３８内に絞り体４０がはめ込まれており、この絞り体４０は、絞りばね４２によって流体室２４への方向で絞りシート４４に向かって押し付けられている。   A throttle 36 is formed in the valve body 34 by inserting the valve body 34 from the throttle opening 38 in the longitudinal direction of the outlet passage 30. A throttle body 40 is fitted in the throttle opening 38, and the throttle body 40 is pressed against the throttle sheet 44 in the direction toward the fluid chamber 24 by a throttle spring 42.

従って、流体室２４から流体を導出する際に、絞り体４０は液圧式の流れ抵抗として作用し、この流れ抵抗は、絞り開口３８を通る流体の流出をできるだけ阻止する。このような形式で流体が流体室２４内でせき止められ、減衰器ダイヤフラム２０は減衰器ハウジング１４に向かって押し退けられる。この場合、減衰器室２６内に弾性的に圧縮可能なガスが存在する。このガスによっておよび減衰器ダイヤフラム２０自体の弾性によって、供給路２８を通って供給されその際に部分的に圧力脈動に晒される流体のために、圧力波を減衰する作用が得られる。   Therefore, when the fluid is led out from the fluid chamber 24, the throttle body 40 acts as a hydraulic flow resistance, and this flow resistance prevents the fluid from flowing out through the throttle opening 38 as much as possible. In this manner, fluid is damped in the fluid chamber 24 and the attenuator diaphragm 20 is displaced toward the attenuator housing 14. In this case, elastically compressible gas exists in the attenuator chamber 26. Due to this gas and due to the elasticity of the attenuator diaphragm 20 itself, the action of attenuating the pressure wave is obtained for the fluid that is supplied through the supply channel 28 and is in this case partially exposed to pressure pulsations.

絞り３６の手前でせき止められる流体が増大するにつれて、流体室の室体積が次第に拡大し、それと同時に減衰器室２６の室体積が次第に縮小する。減衰器室２６の室体積が最終的にほぼゼロになると直ちに、減衰装置１０はその機能をほぼ失う。しかしながらそれと同時に、絞り３６の絞り機能若しくはせき止め機能は基本的に維持される。このような絞り３６の機能、およびそれに伴う、減衰装置１０を貫通ガイドされる流体のための流動損失を減少させるために、および避けるために、減衰器ダイヤフラム２０を弁体３４に機械的に連結するタイロッド４６が設けられている。   As the fluid blocked before the restriction 36 increases, the chamber volume of the fluid chamber gradually increases and at the same time the chamber volume of the attenuator chamber 26 gradually decreases. As soon as the chamber volume of the attenuator chamber 26 eventually becomes nearly zero, the attenuator 10 loses its function. However, at the same time, the diaphragm function or the damming function of the diaphragm 36 is basically maintained. In order to reduce and avoid the function of such a restriction 36 and the associated flow loss for the fluid guided through the damping device 10, the attenuator diaphragm 20 is mechanically connected to the valve body 34. A tie rod 46 is provided.

タイロッド４６によって連結されていることにより、弁体３４は減衰器室２６の室体積が次第に縮小するにつれてバルブシート３２から持ち上げられ、このような形式で弁体３４とバルブシート３２との間でバイパス４８が開放される。次いで、このバイパス４８を通って流体が、絞り作用に晒されることなく、流体室２４から流出することができる。   By being connected by the tie rod 46, the valve body 34 is lifted from the valve seat 32 as the chamber volume of the attenuator chamber 26 gradually decreases, and in this manner, the valve body 34 is bypassed between the valve body 34 and the valve seat 32. 48 is opened. The fluid can then flow out of the fluid chamber 24 through this bypass 48 without being exposed to the squeezing action.

図２には、図１に示した実施例と構造的に概ね同じである減衰装置１０の実施例が示されている。しかしながら、減衰器ダイヤフラム２０の代わりに、図２に示した実施例では減衰器ピストン５０が設けられており、この減衰器ピストン５０は、らせん状の弾性的な減衰器ばね５２によって絞り３６に向かって押しやられている。減衰器ピストン５０は、流体室２４を減衰器室２６から分離し、この場合、減衰器ばね５２は減衰器室２６内に位置している。   FIG. 2 shows an embodiment of an attenuation device 10 that is substantially the same in structure as the embodiment shown in FIG. However, instead of the attenuator diaphragm 20, in the embodiment shown in FIG. 2, an attenuator piston 50 is provided, which is directed towards the throttle 36 by a helical elastic attenuator spring 52. Have been pushed away. The attenuator piston 50 separates the fluid chamber 24 from the attenuator chamber 26, where the attenuator spring 52 is located within the attenuator chamber 26.

所属の絞り体４０は、牽引ロープ５４によって減衰器ピストン５０に機械的に連結されている。この場合、牽引ロープ５４はその弾性およびその長さに関連して、特別に適合されており、従って、減衰器内室１８内における減衰器ピストン５０の位置に応じて、それによって形成されたバイパス４８のためにそれぞれ所望の開放横断面が得られる。   The associated throttle body 40 is mechanically connected to the attenuator piston 50 by a traction rope 54. In this case, the traction rope 54 is specially adapted in relation to its elasticity and its length, and therefore the bypass formed thereby depending on the position of the attenuator piston 50 in the attenuator chamber 18. For each 48, the desired open cross section is obtained.

図３は、同様に減衰器ハウジング１４内で減衰器ピストン５０がしゅう動可能かつ気密に支承されている、減衰装置１０の実施例を示す。減衰器ピストン５０に、牽引パイプ５６が絞り３６に向かって突き出して配置されている。この牽引パイプ５６によって、図３で見て弁体３４の上方の端部領域が、バイパス４８を提供するために牽引パイプ５６が弁体３４を持ち上げ、この際にバルブシート３２から持ち上げることができるように、把持されている。牽引パイプ５６が、体積が非常に小さい流体室２４において十分な運動スペースが得られるようにするために、さらに弁体３４が、下方に突き出す中空円筒形の切欠５８によって包囲されている。   FIG. 3 shows an embodiment of the damping device 10 in which the attenuator piston 50 is also slidably and airtightly supported in the attenuator housing 14. A traction pipe 56 is disposed on the attenuator piston 50 so as to protrude toward the throttle 36. With this traction pipe 56, the end region above the valve body 34 as viewed in FIG. 3 allows the traction pipe 56 to lift the valve body 34 to provide a bypass 48 and in this case lift from the valve seat 32. So that it is gripped. In order for the traction pipe 56 to have sufficient movement space in the fluid chamber 24 with a very small volume, the valve body 34 is further surrounded by a hollow cylindrical cutout 58 protruding downward.

１０ 減衰装置
２０減衰器ダイヤフラム
２６ 減衰器室
３２ バルブシート
３４ 弁体
３６ 絞り
４６ タイロッド
４８ バイパス
５０ 減衰器ピストン
５４ 牽引ロープ
５６ 牽引パイプ DESCRIPTION OF SYMBOLS 10 Attenuator 20 Attenuator diaphragm 26 Attenuator chamber 32 Valve seat 34 Valve body 36 Throttle 46 Tie rod 48 Bypass 50 Attenuator piston 54 Tow rope 56 Tow pipe

Claims (10)

室体積が可変である減衰器室（２６）と、該減衰器室（２６）に後置接続された絞り（３６）とを有する、車両ブレーキ装置の液圧ユニットの減衰装置（１０）において、
前記絞り（３６）が可変な絞り作用を有していて、該絞り作用が前記室体積に依存して可変であることを特徴とする、液圧ユニットの減衰装置。 In a damping device (10) for a hydraulic unit of a vehicle brake device, comprising: an attenuator chamber (26) having a variable chamber volume; and a throttle (36) connected downstream of the attenuator chamber (26).
A damping device for a hydraulic unit, characterized in that the throttle (36) has a variable throttle action, the throttle action being variable depending on the chamber volume. 前記絞り作用が、前記室体積の拡大につれて減少することを特徴とする、請求項１記載の減衰装置。   The damping device according to claim 1, wherein the throttle action decreases as the chamber volume increases. 前記絞り作用が、前記室体積の最大時において概ねゼロに減少することを特徴とする、請求項２記載の減衰装置。   3. A damping device according to claim 2, characterized in that the throttling action decreases to approximately zero at the maximum of the chamber volume. 前記減衰器室（２６）が変形可能な減衰器ダイヤフラム（２０）によって画成されていて、前記絞り（３６）の絞り作用が前記減衰器ダイヤフラム（２０）の変形状態に依存して可変であることを特徴とする、請求項１から３までのいずれか１項記載の減衰装置。   The attenuator chamber (26) is defined by a deformable attenuator diaphragm (20), and the throttling action of the diaphragm (36) is variable depending on the deformation state of the attenuator diaphragm (20). The attenuation device according to any one of claims 1 to 3, characterized in that: 前記減衰器室（２６）が位置調節可能な減衰器ピストン（５０）によって画成されていて、前記絞り（３６）の絞り作用が前記減衰器ピストン（５０）の調節位置に依存して可変であることを特徴とする、請求項１から３までのいずれか１項記載の減衰装置。   The attenuator chamber (26) is defined by a position-adjustable attenuator piston (50), and the throttling action of the restrictor (36) is variable depending on the adjustment position of the attenuator piston (50). The damping device according to claim 1, wherein the damping device is provided. 前記絞り（３６）に対してバイパスが並列接続されており、前記バイパスにおいて、前記絞り（３６）の絞り作用を変えるために、前記バイパス（４８）の大きさが前記室体積に依存して可変であることを特徴とする、請求項１から５までのいずれか１項記載の減衰装置。   A bypass is connected in parallel to the throttle (36). In the bypass, the size of the bypass (48) is variable depending on the chamber volume in order to change the throttle action of the throttle (36). The attenuation device according to any one of claims 1 to 5, characterized in that: 前記バイパス（４８）が弁体（３４）によって閉鎖可能であって、前記弁体（３４）がバルブシート（３２）に対してシールされていることを特徴とする、請求項６記載の減衰装置。   The damping device according to claim 6, characterized in that the bypass (48) is closable by a valve body (34), the valve body (34) being sealed against the valve seat (32). . 前記絞り（３６）が前記弁体（３４）内に配置されていることを特徴とする、請求項６または７記載の減衰装置。   The damping device according to claim 6 or 7, characterized in that the throttle (36) is arranged in the valve body (34). 前記弁体（３４）が室体積に依存して機械的な連結エレメントによって移動可能であり、この場合、前記連結エレメントが特に前記減衰器ダイヤフラム（２０）または前記減衰器ピストン（５０）に連結されていることを特徴とする、請求項７または８記載の減衰装置。   The valve body (34) can be moved by a mechanical connecting element depending on the chamber volume, in which case the connecting element is connected in particular to the attenuator diaphragm (20) or the attenuator piston (50). 9. A damping device according to claim 7 or 8, characterized in that 前記連結エレメントが、引張エレメントとして、特にタイロッド（４６）、牽引ロープ（５４）または牽引パイプ（５６）として構成されていることを特徴とする、請求項９記載の減衰装置。   10. Damping device according to claim 9, characterized in that the connecting element is configured as a tension element, in particular as a tie rod (46), a traction rope (54) or a traction pipe (56).
JP2018134248A 2017-08-02 2018-07-17 Damping device for hydraulic unit of vehicle braking system with damper chamber Active JP7197299B2 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102017213322.8 2017-08-02
DE102017213322.8A DE102017213322A1 (en) 2017-08-02 2017-08-02 Damper device of a hydraulic unit of a vehicle brake device with a damper chamber

Publications (2)

Publication Number Publication Date
JP2019051925A true JP2019051925A (en) 2019-04-04
JP7197299B2 JP7197299B2 (en) 2022-12-27

Family

ID=65020141

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2018134248A Active JP7197299B2 (en) 2017-08-02 2018-07-17 Damping device for hydraulic unit of vehicle braking system with damper chamber

Country Status (3)

Country Link
JP (1) JP7197299B2 (en)
CN (1) CN109383479B (en)
DE (1) DE102017213322A1 (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2020189218A1 (en) 2019-03-19 2020-09-24 富士フイルム株式会社 Cell culture system and cell culture method
CN114502437A (en) * 2019-10-17 2022-05-13 大陆-特韦斯贸易合伙股份公司及两合公司 Pulsation damper

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102019207686A1 (en) * 2019-05-25 2020-11-26 Robert Bosch Gmbh Hydraulic unit, in particular for supplying a brake circuit of a vehicle brake system with pressure medium under brake pressure
DE102019209892A1 (en) * 2019-07-04 2021-01-07 Robert Bosch Gmbh Brake system damper with another space

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2011005887A (en) * 2009-06-23 2011-01-13 Advics Co Ltd Damper device and brake fluid pressure control device
US20160176387A1 (en) * 2014-12-16 2016-06-23 Robert Bosch Gmbh Pressure Change Damper for a Hydraulic Vehicle Brake System with Brake Force Control, and Hydraulic Vehicle Brake System with Brake Force Control with such a Pressure Change Damper

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3923282C2 (en) * 1989-07-14 1998-04-30 Bosch Gmbh Robert Device for damping pressure vibrations
DE9112163U1 (en) * 1991-09-30 1993-01-28 Robert Bosch Gmbh, 7000 Stuttgart Throttle with pressure relief valve to dampen pressure oscillations
JP2004090843A (en) * 2002-09-03 2004-03-25 Nissin Kogyo Co Ltd Vehicular brake device
DE10305310B4 (en) 2003-02-10 2005-11-24 Robert Bosch Gmbh Device for damping pressure pulsations
JP2008290618A (en) * 2007-05-25 2008-12-04 Nissin Kogyo Co Ltd Pump device
DE102008003454A1 (en) * 2008-01-08 2009-07-09 Robert Bosch Gmbh Hydraulic fluid pump with a sealing element
DE102010040193B4 (en) * 2010-09-03 2021-07-22 Robert Bosch Gmbh Piston pump with a discharge
JP5421946B2 (en) * 2011-03-11 2014-02-19 本田技研工業株式会社 Hydraulic pressure generator for vehicles
DE102011089183A1 (en) * 2011-12-20 2013-06-20 Robert Bosch Gmbh Pressure pulsation damper for a vehicle brake system
DE102014212501A1 (en) * 2014-06-27 2015-12-31 Robert Bosch Gmbh Valve of a piston pump with a two-part closing body
DE102014220368A1 (en) * 2014-10-08 2016-04-14 Robert Bosch Gmbh Piston pump for a hydraulic vehicle brake system
DE102014224829A1 (en) * 2014-12-04 2016-06-09 Robert Bosch Gmbh Pressure change damper for a slip-controlled, hydraulic vehicle brake system and vehicle brake system with such a pressure change damper

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2011005887A (en) * 2009-06-23 2011-01-13 Advics Co Ltd Damper device and brake fluid pressure control device
US20160176387A1 (en) * 2014-12-16 2016-06-23 Robert Bosch Gmbh Pressure Change Damper for a Hydraulic Vehicle Brake System with Brake Force Control, and Hydraulic Vehicle Brake System with Brake Force Control with such a Pressure Change Damper

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2020189218A1 (en) 2019-03-19 2020-09-24 富士フイルム株式会社 Cell culture system and cell culture method
CN114502437A (en) * 2019-10-17 2022-05-13 大陆-特韦斯贸易合伙股份公司及两合公司 Pulsation damper

Also Published As

Publication number Publication date
CN109383479A (en) 2019-02-26
JP7197299B2 (en) 2022-12-27
DE102017213322A1 (en) 2019-02-07
CN109383479B (en) 2021-06-22

Similar Documents

Publication Publication Date Title
JP2019051925A (en) Damper device of hydraulic unit of vehicle brake device with damper chamber
KR102137287B1 (en) Damping force adjustable damper
JP6130684B2 (en) Solenoid valve
US20120048665A1 (en) Compression isolator for a suspension damper
US9970505B2 (en) Shock absorber
KR102508991B1 (en) Brake system
US20160160955A1 (en) Suspension damper
EP2977641A1 (en) Shock absorber
US10508754B2 (en) Valve device for throttling a pressure medium flow, and damping device for damping pressure pulsations
WO2017013960A1 (en) Shock absorber
WO2014125974A1 (en) Solenoid valve
JP2015059641A (en) Shock absorber
DE102010040193A1 (en) Piston pump with an outflow
CN109642684B (en) Damping valve and cylinder device
CN111810500B (en) Hydraulic amplifier arrangement
CN110107765B (en) Self-adaptive compound pressure pulsation attenuator
JP2017506598A (en) Damping device and vehicle brake device capable of slip control
CN108150472B (en) A kind of buffer overflow valve
JP6059549B2 (en) Solenoid valve
JP6271767B2 (en) Attenuator
TW201809500A (en) Cylinder device
US3036436A (en) Fluid pressure control apparatus
JP2015209203A (en) Hydraulic device equipped with damper for vehicle brake device
JP5733472B2 (en) Hydraulic control valve and hydraulic control device
JP2022147806A (en) Fluid shock absorber

Legal Events

Date Code Title Description
A621 Written request for application examination

Free format text: JAPANESE INTERMEDIATE CODE: A621

Effective date: 20210628

A977 Report on retrieval

Free format text: JAPANESE INTERMEDIATE CODE: A971007

Effective date: 20220617

A131 Notification of reasons for refusal

Free format text: JAPANESE INTERMEDIATE CODE: A131

Effective date: 20220624

A601 Written request for extension of time

Free format text: JAPANESE INTERMEDIATE CODE: A601

Effective date: 20220916

A521 Request for written amendment filed

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20221103

TRDD Decision of grant or rejection written
A01 Written decision to grant a patent or to grant a registration (utility model)

Free format text: JAPANESE INTERMEDIATE CODE: A01

Effective date: 20221206

A61 First payment of annual fees (during grant procedure)

Free format text: JAPANESE INTERMEDIATE CODE: A61

Effective date: 20221215

R150 Certificate of patent or registration of utility model

Ref document number: 7197299

Country of ref document: JP

Free format text: JAPANESE INTERMEDIATE CODE: R150