JP6496516B2 - High pressure fuel supply pump - Google Patents
High pressure fuel supply pump Download PDFInfo
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- JP6496516B2 JP6496516B2 JP2014212187A JP2014212187A JP6496516B2 JP 6496516 B2 JP6496516 B2 JP 6496516B2 JP 2014212187 A JP2014212187 A JP 2014212187A JP 2014212187 A JP2014212187 A JP 2014212187A JP 6496516 B2 JP6496516 B2 JP 6496516B2
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- damper
- cover
- holding member
- damper cover
- fuel supply
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- 239000000446 fuel Substances 0.000 title claims description 63
- 230000033001 locomotion Effects 0.000 claims description 6
- 238000007906 compression Methods 0.000 claims description 4
- 230000006835 compression Effects 0.000 claims description 3
- 238000000034 method Methods 0.000 description 11
- 230000005284 excitation Effects 0.000 description 7
- 230000007246 mechanism Effects 0.000 description 7
- 230000000694 effects Effects 0.000 description 6
- 239000012528 membrane Substances 0.000 description 6
- 238000002485 combustion reaction Methods 0.000 description 3
- 230000002093 peripheral effect Effects 0.000 description 3
- XKRFYHLGVUSROY-UHFFFAOYSA-N Argon Chemical compound [Ar] XKRFYHLGVUSROY-UHFFFAOYSA-N 0.000 description 2
- 230000007423 decrease Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 238000002347 injection Methods 0.000 description 2
- 239000007924 injection Substances 0.000 description 2
- 239000002184 metal Substances 0.000 description 2
- 230000010349 pulsation Effects 0.000 description 2
- 230000005855 radiation Effects 0.000 description 2
- 238000010521 absorption reaction Methods 0.000 description 1
- 229910052786 argon Inorganic materials 0.000 description 1
- 230000001174 ascending effect Effects 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 230000008602 contraction Effects 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 238000013016 damping Methods 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 239000002828 fuel tank Substances 0.000 description 1
- 239000011261 inert gas Substances 0.000 description 1
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- Fuel-Injection Apparatus (AREA)
Description
本発明は，内燃機関に用いられる高圧燃料供給ポンプに関する。 The present invention relates to a high-pressure fuel supply pump used for an internal combustion engine.
近年，快適性向上の観点から高圧燃料供給ポンプに対する静粛性のニーズが高まっている。高圧燃料供給ポンプの静粛性,特に，ダンパカバーからの放射音の低減に関する技術として以下のような発明が開示されている。 In recent years, the need for quietness for high-pressure fuel supply pumps is increasing from the viewpoint of improving comfort. The following inventions have been disclosed as techniques relating to the quietness of the high-pressure fuel supply pump, in particular, the reduction of radiation noise from the damper cover.
特開2012-132400号公報(特許文献1)には，ダンパカバーとダンパ側支持部材の間に，波ワッシャと燃圧によって弾性変形可能な円環状の弾性部材で振動を抑制している。(段落0009，図2) In Japanese Patent Laid-Open No. 2012-132400 (Patent Document 1), vibration is suppressed between a damper cover and a damper-side support member by a wave washer and an annular elastic member that can be elastically deformed by fuel pressure. (Paragraph 0009, Figure 2)
特許文献１の高圧燃料供給ポンプでは，ダンパからダンパカバーへの振動の減衰に，波ワッシャと円環状の弾性部材の2部材を用いている。また，波ワッシャとダンパカバーとはポンプの上下方向，つまり，プランジャの軸方向で接触しており，ダンパカバーへの軸方向加振力はそのまま伝達される。そのため，波ワッシャとの接触部を起点とした膜振動モードが励起されるため，このままでは，ポンプの上下方向にダンパカバーが振動するモードを抑制することは困難であると考えられる。本発明は，このような点を鑑みて改良したものであり，本発明の主な目的はダンパカバーの振動および放射音を低減することである。 In the high-pressure fuel supply pump of Patent Document 1, two members, a wave washer and an annular elastic member, are used for damping vibration from the damper to the damper cover. In addition, the wave washer and the damper cover are in contact with each other in the vertical direction of the pump, that is, in the axial direction of the plunger, and the axial excitation force to the damper cover is transmitted as it is. Therefore, since the membrane vibration mode starting from the contact portion with the wave washer is excited, it is considered difficult to suppress the mode in which the damper cover vibrates in the vertical direction of the pump. The present invention has been improved in view of the above points, and a main object of the present invention is to reduce vibration and radiated sound of the damper cover.
上記目的を達成するための本発明の高圧燃料供給ポンプは，その一例としてダンパカバーとダンパとの間にダンパ保持部材を備え，前記ダンパ保持部材が、前記ダンパカバーの凸部の内側面と複数点または面で接触し、かつ前記ダンパカバーの凸部の上面と側面に接触し、前記ダンパ保持部材の前記ダンパカバーと接触しない部分は、円形で断面が波型形状の部材とすることで実現できる。
High-pressure fuel supply pump of the present invention for achieving the above object, comprises a damper holding member between the damper cover and the damper as an example, the damper holding member, an inner surface and a plurality of convex portions of the damper cover The part that contacts at the point or the surface, contacts the upper surface and the side surface of the convex portion of the damper cover, and does not contact the damper cover of the damper holding member is realized by a circular member having a corrugated cross section. it can.
本発明によれば，ダンパからダンパカバーへの振動を抑制できるので，ダンパカバーの振動および放射音を低減できる。 According to the present invention, since vibration from the damper to the damper cover can be suppressed, vibration of the damper cover and radiated sound can be reduced.
上記した以外の課題，構成及び効果は，以下の実施形態の説明により明らかにされる。 Problems, configurations, and effects other than those described above will be clarified by the following description of embodiments.
以下，本発明係る実施例を説明する。 Examples according to the present invention will be described below.
以下に添付の図を参照して本発明の実施形態について詳細に説明する。図1は本発明に係る実施例1の高圧燃料供給ポンプの全体構造を示す縦断面図である。図２は，本発明に係る実施例1の高圧燃料供給ポンプの底面図であり，図１は，本図のＡＡ断面図である。図３は，本発明に係る実施例１の高圧供給燃料ポンプを用いた燃料供給システムの一例を示すシステム構成図である。 Hereinafter, embodiments of the present invention will be described in detail with reference to the accompanying drawings. FIG. 1 is a longitudinal sectional view showing the overall structure of a high-pressure fuel supply pump according to a first embodiment of the present invention. FIG. 2 is a bottom view of the high-pressure fuel supply pump according to the first embodiment of the present invention, and FIG. 1 is a cross-sectional view taken along the line AA in FIG. FIG. 3 is a system configuration diagram illustrating an example of a fuel supply system using the high-pressure supply fuel pump according to the first embodiment of the present invention.
図3を用いて，まず，高圧燃料供給ポンプのシステム構成について説明する。 First, the system configuration of the high-pressure fuel supply pump will be described with reference to FIG.
同図の破線で囲まれた部分は高圧燃料供給ポンプの本体を示し，本枠線内に含まれている機構や部品は高圧燃料供給ポンプ本体1に一体に組み込まれている。燃料タンク２０内の燃料はフィードポンプ２１によって汲み上げられ，吸入配管２８を通してポンプ本体１の吸入ジョイント１０ａに送られる。 A portion surrounded by a broken line in the figure shows the main body of the high-pressure fuel supply pump, and the mechanisms and components included in the frame are integrated into the high-pressure fuel supply pump main body 1. The fuel in the fuel tank 20 is pumped up by the feed pump 21 and sent to the suction joint 10 a of the pump body 1 through the suction pipe 28.
吸入ジョイント１０ａを通過した燃料は圧力低減機構であるダンパ９，吸入通路１０ｂを介して容量可変機構を構成する吸入弁３０の吸入ポート３０ａに送られる。 The fuel that has passed through the suction joint 10a is sent to a suction port 30a of a suction valve 30 that constitutes a variable capacity mechanism via a damper 9 that is a pressure reduction mechanism and a suction passage 10b.
吸入弁３０は，電磁コイル３０８を備え，電磁コイル３０８が通電されない時は，アンカーばね３０３の付勢力と弁ばね３０４の付勢力の差により，吸入弁体３０１は開弁方向に付勢され吸入口３０ｄは開の状態になっている。なお，アンカーばね３０３の付勢力は，弁ばねの付勢力３０４より大きくなるように設定されている。 The intake valve 30 includes an electromagnetic coil 308. When the electromagnetic coil 308 is not energized, the intake valve body 301 is urged in the valve opening direction due to the difference between the urging force of the anchor spring 303 and the urging force of the valve spring 304. The mouth 30d is in an open state. The biasing force of the anchor spring 303 is set to be larger than the biasing force 304 of the valve spring.
電磁コイル３０８が通電されている状態では，アンカー３０５は同図の左方に移動した状態で，アンカーばね３０３が圧縮された状態が維持される。電磁プランジャ３０５の先端が同軸で接触するように取り付けられた吸入弁体３０１は弁ばね３０４の付勢力により高圧燃料供給ポンプの加圧室１１につながる吸入口３０ｄを閉じている。 In a state where the electromagnetic coil 308 is energized, the anchor spring 305 is moved to the left in the figure, and the state in which the anchor spring 303 is compressed is maintained. The suction valve body 301 attached so that the tip of the electromagnetic plunger 305 contacts coaxially closes the suction port 30d connected to the pressurizing chamber 11 of the high-pressure fuel supply pump by the biasing force of the valve spring 304.
次に，高圧燃料供給ポンプの動作について説明する。 Next, the operation of the high pressure fuel supply pump will be described.
プランジャ２の下端に設置されているカム(図示していない)の回転により，プランジャ２が下方へ変位している吸入工程状態にある時は，加圧室１１の容積は増加し加圧室内の燃料圧力が低下する。この工程で加圧室１１内の燃料圧力が吸入通路１０ｂ(吸入ポート３０ａ)の圧力よりも低くなると，燃料は，開口状態にある吸入口３０ｄを通り加圧室１１に流入する。 When the plunger (2) is displaced downward due to the rotation of a cam (not shown) installed at the lower end of the plunger 2, the volume of the pressurizing chamber 11 increases to increase the volume of the pressurizing chamber 11. Fuel pressure decreases. In this step, when the fuel pressure in the pressurizing chamber 11 becomes lower than the pressure in the suction passage 10b (suction port 30a), the fuel flows into the pressurizing chamber 11 through the suction port 30d in the open state.
吸入工程を終了し圧縮工程へと移行した場合，プランジャ２は，上方へ移動する状態へ移る。ここで，電磁コイル３０８は無通電状態を維持したままであり，磁気付勢力は作用しない。従って，吸入弁体３０１はアンカーばね３０３の付勢力により開弁したままである。加圧室１１の容積は，プランジャ２の圧縮運動に伴い減少するが，この状態では，一度，加圧室１１に吸入された燃料が，再び，開弁状態の吸入弁体３０１と通して吸入通路１０ｂ(吸入ポート３０ａ)へと戻されるので，加圧室１１の圧力が上昇することはない。この工程を戻し工程と称する。 When the suction process is finished and the process proceeds to the compression process, the plunger 2 moves to a state of moving upward. Here, the electromagnetic coil 308 remains in a non-energized state, and no magnetic biasing force acts. Therefore, the suction valve body 301 remains open due to the biasing force of the anchor spring 303. The volume of the pressurizing chamber 11 decreases with the compression movement of the plunger 2. In this state, the fuel once sucked into the pressurizing chamber 11 is sucked again through the intake valve body 301 in the valve open state. Since the pressure is returned to the passage 10b (suction port 30a), the pressure in the pressurizing chamber 11 does not increase. This process is called a return process.
この状態で，エンジンコントロールユニット２７からの制御信号が吸入弁３０に印加されると吸入弁３０の電磁コイル３０８には電流が流れ，磁気付勢力により電磁プランジャ３０５が左方向へ移動し，アンカーばね３０３が圧縮された状態が維持される。その結果，吸入弁体３０１にはアンカーばね３０３の付勢力が作用しなくなり，弁ばね３０４による付勢力と，燃料が吸入通路１０ｂ(吸入ポート３０ａ)に流れ込むことによる流体力が働くため，吸入弁３０１は閉弁し吸入口３０ｄを閉じる。吸入口３０ｄが閉じると，そのときから加圧室１１の燃料圧力はプランジャ２の上昇運動と共に上昇する。そして，燃料吐出口１２の圧力以上になると，吐出弁８を介して加圧室１１に残っている燃料の高圧吐出が行われ，コモンレール２３へと供給される。この工程を吐出工程と称する。 In this state, when a control signal from the engine control unit 27 is applied to the suction valve 30, a current flows through the electromagnetic coil 308 of the suction valve 30, and the electromagnetic plunger 305 moves to the left by the magnetic biasing force, and the anchor spring The state where 303 is compressed is maintained. As a result, the biasing force of the anchor spring 303 does not act on the suction valve body 301, and the biasing force of the valve spring 304 and the fluid force due to the fuel flowing into the suction passage 10b (suction port 30a) work. 301 closes and closes the inlet 30d. When the suction port 30d is closed, the fuel pressure in the pressurizing chamber 11 rises with the upward movement of the plunger 2 from that time. When the pressure exceeds the pressure of the fuel discharge port 12, high pressure discharge of the fuel remaining in the pressurizing chamber 11 is performed via the discharge valve 8 and supplied to the common rail 23. This process is called a discharge process.
以上のことから，プランジャが下死点から上死点まで移動する上昇工程は，戻し工程と吐出工程からなることがわかる。また，吸入弁３０の電磁コイル３０８への通電タイミングを制御することにより，吐出される高圧燃料の量を制御することができることがわかる。 From the above, it can be seen that the ascending process in which the plunger moves from the bottom dead center to the top dead center includes the return process and the discharge process. It can also be seen that the amount of high-pressure fuel discharged can be controlled by controlling the energization timing of the electromagnetic coil 308 of the intake valve 30.
一方，加圧室１１の出口には吐出弁８が設けられている。吐出弁８は，吐出弁シート８ａ，吐出弁８ｂ，吐出弁ばね８ｃを備え，加圧室１１と燃料吐出口１２に燃料差圧が無い状態では，吐出弁８ｂは吐出弁ばね８ｃによる付勢力で吐出弁シート８ａに圧着され閉弁状態となっている。加圧室１１の燃料圧力が，燃料吐出口１２の燃料圧力より大きくなった時に始めて，吐出弁８ｂは吐出弁ばね８ｃに逆らって開弁し，加圧室１１内の燃料は燃料吐出口１２を経てコモンレール２３へと高圧吐出される。 On the other hand, a discharge valve 8 is provided at the outlet of the pressurizing chamber 11. The discharge valve 8 includes a discharge valve seat 8a, a discharge valve 8b, and a discharge valve spring 8c. When there is no fuel differential pressure in the pressurizing chamber 11 and the fuel discharge port 12, the discharge valve 8b is biased by the discharge valve spring 8c. Is pressed against the discharge valve seat 8a and is in a closed state. Only when the fuel pressure in the pressurizing chamber 11 becomes higher than the fuel pressure in the fuel discharge port 12, the discharge valve 8 b opens against the discharge valve spring 8 c, and the fuel in the pressurization chamber 11 is discharged from the fuel discharge port 12. After that, high pressure is discharged to the common rail 23.
以上のように，吸入ジョイント１０ａに導かれた燃料は，ポンプ本体１の加圧室１１において，プランジャ２の往復運動によって必要な量が加圧され，燃料吐出口１２からコモンレール２３に圧送される。なお，コモンレール２３には，直接噴射用インジェクタ24，圧力センサ２６が装着されている。直接噴射インジェクタ24は，内燃機関の気筒数に合わせて装着されており，エンジンコントロールユニット２７の制御信号によって開閉弁して，燃料をシリンダ内に噴射する。 As described above, the fuel guided to the suction joint 10 a is pressurized in the pressurizing chamber 11 of the pump body 1 by the reciprocating motion of the plunger 2 and is pumped from the fuel discharge port 12 to the common rail 23. . The common rail 23 is provided with a direct injection injector 24 and a pressure sensor 26. The direct injection injectors 24 are mounted according to the number of cylinders of the internal combustion engine, and are opened and closed by a control signal from the engine control unit 27 to inject fuel into the cylinders.
以下に，本実施例に係る高圧燃料供給ポンプの構成や動作を図1を用いて説明する。 Hereinafter, the configuration and operation of the high-pressure fuel supply pump according to this embodiment will be described with reference to FIG.
一般的に，高圧燃料供給ポンプは，内燃機関のシリンダヘッド(図に示していない)に密着してフランジ１０１を介して固定される。 In general, the high-pressure fuel supply pump is fixed to the cylinder head (not shown) of the internal combustion engine through a flange 101 in close contact with the cylinder head.
ポンプ本体1には，プランジャ２の往復運動をガイドし，かつ，内部に加圧室１１を形成するように端部が有底筒型状に形成されたシリンダ６が取り付けられている。さらに，燃料を供給するための吸入弁３０と，加圧室１１からの燃料を吐出するための吐出弁８と，燃料の圧力が一定値を超えた場合に開弁するリリーフ弁機構１００(図に示していない)を備えている。（図示されていないのはリリーフ機構で吐出機構は図示されているのでは？必要に応じて記載を修正下さい。）
ポンプ本体１とダンパカバー１４との結合によってダンパ室１０が形成され，ダンパ室１０には，高圧燃料供給ポンプ内で発生した圧力脈動を低減させるためのダンパ９が設置されている。ダンパ９は，波板状の円盤型金属板２枚を外周で貼り合わせ，内部にアルゴンのような不活性ガスを注入した金属ダンパで形成されており，圧力脈動はダンパ９の膨張・収縮により吸収低減される。
The pump body 1 is provided with a cylinder 6 that guides the reciprocating motion of the plunger 2 and has an end formed in a bottomed cylindrical shape so as to form a pressurizing chamber 11 therein. Furthermore, a suction valve 30 for supplying fuel, a discharge valve 8 for discharging fuel from the pressurizing chamber 11, and a relief valve mechanism 100 that opens when the fuel pressure exceeds a certain value (see FIG. Not shown). (The relief mechanism is not shown in the figure, and the discharge mechanism is shown in the figure. Correct the description if necessary.)
A damper chamber 10 is formed by coupling the pump body 1 and the damper cover 14, and a damper 9 is installed in the damper chamber 10 for reducing pressure pulsation generated in the high-pressure fuel supply pump. The damper 9 is formed of a metal damper in which two corrugated disk-shaped metal plates are bonded together on the outer periphery, and an inert gas such as argon is injected therein, and pressure pulsation is caused by expansion / contraction of the damper 9. Absorption is reduced.
ここで，ダンパ９とダンパカバー１４は，ダンパ保持部材１４１を介して接続されている。これにより，ダンパ９からダンパカバー１４への振動を抑制できるので，ダンパカバー１４での振動および放射音を低減できる。 Here, the damper 9 and the damper cover 14 are connected via a damper holding member 141. Thereby, since the vibration from the damper 9 to the damper cover 14 can be suppressed, the vibration and radiation sound in the damper cover 14 can be reduced.
本実施例のダンパ保持部材１４１の構造や効果について，図4から図６を用いて詳細に説明する。図4は，図1のダンパ保持部材周辺部材の拡大図であり，図５は，本実施例のダンパ保持部材の一例の外観図で，上段が平面図で，下段がＢＢ断面図である。また，図６は，本実施例のダンパ保持部材の斜視図を示している。 The structure and effect of the damper holding member 141 of the present embodiment will be described in detail with reference to FIGS. FIG. 4 is an enlarged view of the damper holding member peripheral member of FIG. 1, and FIG. 5 is an external view of an example of the damper holding member of the present embodiment, where the upper stage is a plan view and the lower stage is a BB sectional view. FIG. 6 shows a perspective view of the damper holding member of this embodiment.
これらの図に示すように，ダンパカバー１４には，外側に突出する凸部１４Ａを有し，その凸部に嵌まり込むような形でダンパ保持部材１４１が介在する。つまり，ダンパ保持部材１４１にも凸部形状を有しており，その外側面がダンパカバー１４の凸部の内側面にほぼ均等に接触するように取り付けられている。 As shown in these drawings, the damper cover 14 has a protruding portion 14A that protrudes outward, and a damper holding member 141 is interposed so as to fit into the protruding portion. That is, the damper holding member 141 also has a convex shape, and is attached so that the outer surface thereof is in contact with the inner surface of the convex portion of the damper cover 14 almost evenly.
従って，ダンパ保持部材１４１からの加振力は，ダンパ保持部材１４１の上面と側面からダンパカバー１４に伝達する。これは，ダンパ保持部材１４１の加振力をダンパカバー１４の上面と側面で受けることであり，加振力を上面と側面に分散すると言い換えることができる。ここで言う，上面方向は，ポンプの上下方向つまり軸方向に相当し，側面方向は，ポンプの左右方向つまり径方向に相当する。以下，前者を軸方向，後者を径方向で表記を統一する。 Therefore, the excitation force from the damper holding member 141 is transmitted to the damper cover 14 from the upper surface and side surface of the damper holding member 141. In other words, the excitation force of the damper holding member 141 is received by the upper surface and the side surface of the damper cover 14, and in other words, the excitation force is distributed to the upper surface and the side surface. Here, the upper surface direction corresponds to the vertical direction of the pump, that is, the axial direction, and the side surface direction corresponds to the horizontal direction of the pump, that is, the radial direction. In the following, the former will be unified in the axial direction and the latter in the radial direction.
本実施例の効果をまとめると以下になる。ダンパカバーからの放射音は，ダンパカバーの膜振動が主要因であり，膜振動はダンパカバーが上下つまり軸方向に振動するモードである。従って，膜振動を低減するには，軸方向振動を低減する必要がある。本実施例では，まず，ダンパカバー１４に凸部を設けることにより，リブ効果によりダンパカバー１４自体の剛性が向上する。また，ダンパ保持部材１４１がダンパ９とダンパカバー１４の間に介在することにより，ダンパ９の振動を直接ダンパカバー１４に伝達しないので，振動抑制効果が得られる。さらに，ダンパカバー１４の凸部の内側でダンパ保持部材１４１を接触させることにより，ダンパカバー１４への加振力つまり振動を軸方向と径方向に分散させて受けているので，径方向に加振力を分散する分だけ軸方向の加振力を低減できる。さらに，ダンパカバー１４とダンパ保持部材１４１を面で接触させることにより，多点で加振力を受けるため加振力が分散されるので，振動が小さくなる。以上のことより，本実施例により，ダンパカバー１４の軸方向振動および放射音を低減でき，膜振動モードを抑制できる。 The effects of this embodiment are summarized as follows. The radiated sound from the damper cover is mainly caused by the membrane vibration of the damper cover, and the membrane vibration is a mode in which the damper cover vibrates up and down, that is, in the axial direction. Therefore, in order to reduce membrane vibration, it is necessary to reduce axial vibration. In the present embodiment, first, by providing a convex portion on the damper cover 14, the rigidity of the damper cover 14 itself is improved by the rib effect. Further, since the damper holding member 141 is interposed between the damper 9 and the damper cover 14, the vibration of the damper 9 is not directly transmitted to the damper cover 14, thereby obtaining a vibration suppressing effect. Furthermore, since the damper holding member 141 is brought into contact with the inside of the convex portion of the damper cover 14, the exciting force, that is, the vibration applied to the damper cover 14 is received while being distributed in the axial direction and the radial direction. The axial excitation force can be reduced by the amount of vibration distribution. Further, by bringing the damper cover 14 and the damper holding member 141 into contact with each other on the surface, the vibration is reduced because the vibration is reduced because the vibration is received at multiple points. From the above, according to the present embodiment, the axial vibration and radiated sound of the damper cover 14 can be reduced, and the membrane vibration mode can be suppressed.
ここで，ダンパカバー１４の凸部の位置は，ダンパカバー１４の中心部には限らず，ダンパカバー１４上であればどの場所でもかまわない。また，凸部の形状も円形状でなくとも外側に凸なる部分があればよい。 Here, the position of the convex portion of the damper cover 14 is not limited to the central portion of the damper cover 14, and may be any location on the damper cover 14. Moreover, the shape of the convex portion is not limited to a circular shape, but may be a portion that protrudes outward.
また，これらの図に示すように，ダンパ保持部材１４１のダンパカバー１４と接触しない部分は，波型形状となっており，ダンパ９とは線状で接触している。接触面積の低減により加振力伝達を抑制するとともに，波型形状により振動を減衰することが可能となる。 Further, as shown in these drawings, the portion of the damper holding member 141 that does not contact the damper cover 14 has a corrugated shape and is in contact with the damper 9 in a linear shape. It is possible to suppress the transmission of excitation force by reducing the contact area and to attenuate the vibration by the wave shape.
ダンパカバー１４とダンパ保持部材１４１との接続方法は，カシメやはめあいなどで実現できる。 The connection method between the damper cover 14 and the damper holding member 141 can be realized by caulking or fitting.
正確な図面でなくとも良いので、凸部が円形やその他図形の図も最低もう一つはご用意頂き、その説明をこの部分に追記下さい。 Since it does not have to be an exact drawing, please prepare at least one figure with a rounded convex part or other figure, and add the explanation to this part.
図7に本発明に係る実施例２の高圧燃料ポンプのダンパ保持部材周辺部材の拡大図を示す。同図の上段は側面から見た図，下段は上面から見た図である。同図に示すように，ダンパカバー１４の上面に上面方向に突出する円形状の凸部を有している。ダンパカバー１４の円形凸部の下面には，ダンパ保持部材１４１が接触している。ダンパ保持部材１４１のダンパカバー１４に接触している部分は，ほぼダンパカバー１４と同形状を有しており，接触していない部分は，波型形状を有しており，ダンパ９と線状で接触している。ダンパカバー１４に円形状の凸部を設けることによりダンパカバー１４の剛性が向上し，ダンパ保持部材１４１がダンパー９とダンパカバー１４Ａの間に介在することにより，ダンパ９からの振動を直接ダンパカバー１４に伝達しないので振動抑制効果が得られる。また，ダンパ保持部材１４１の波板形状により振動を減衰することができる。さらに，ダンパカバー１４の円形凸部の内側でダンパ保持部材１４１を接触させることにより，ダンパカバーへの加振力つまり振動を軸方向と径方向に分散して受けているので，径方向に加振力を分散する分だけ軸方向の加振力を低減できる。さらに，ダンパカバー１４とダンパ保持部材１４１を面で接触させることにより，多点で加振力を受けるため加振力が分散されるので，振動が小さくなる。以上のことより，本実施例により，ダンパカバー１４の軸方向振動および放射音を低減でき，膜振動モードを抑制できる。
FIG. 7 shows an enlarged view of a member around the damper holding member of the high pressure fuel pump according to the second embodiment of the present invention. The top of the figure is a view from the side, and the bottom is a view from the top. As shown in the figure, the upper surface of the damper cover 14 has a circular convex portion protruding in the upper surface direction. A damper holding member 141 is in contact with the lower surface of the circular convex portion of the damper cover 14. The portion of the damper holding member 141 that is in contact with the damper cover 14 has substantially the same shape as the damper cover 14, and the portion that is not in contact has a corrugated shape, and is linear with the damper 9. In contact. By providing a circular convex portion on the damper cover 14, the rigidity of the damper cover 14 is improved, and the damper holding member 141 is interposed between the damper 9 and the damper cover 14 </ b> A, so that vibration from the damper 9 is directly applied to the damper cover 14. Therefore, the vibration suppressing effect is obtained. Further, the vibration can be damped by the corrugated plate shape of the damper holding member 141. Further, by bringing the damper holding member 141 into contact with the inside of the circular convex portion of the damper cover 14, the vibration force applied to the damper cover, that is, vibration, is distributed and received in the axial direction and the radial direction. The axial excitation force can be reduced by the amount of vibration distribution. Further, by bringing the damper cover 14 and the damper holding member 141 into contact with each other on the surface, the vibration is reduced because the vibration is reduced because the vibration is received at multiple points. From the above, according to the present embodiment, the axial vibration and radiated sound of the damper cover 14 can be reduced, and the membrane vibration mode can be suppressed.
また、本実施例は以下のようにも表現できる。すなわち、ダンパと、ダンパカバーとを有する高圧燃料供給ポンプであって、ダンパカバーは凸部を有し、ダンパとダンパカバーとの間にダンパ保持部材を備え、該ダンパ保持部材がダンパカバーの凸部と複数点または面で接触する高圧燃料供給ポンプ。言うまでもなく、本実施例は上述した実施例と各構成の組合せが可能である。
The present embodiment can also be expressed as follows. That is, a high-pressure fuel supply pump having a damper and a damper cover, wherein the damper cover has a convex portion, a damper holding member is provided between the damper and the damper cover, and the damper holding member is a convex portion of the damper cover. High-pressure fuel supply pump in contact with multiple parts or surfaces. Needless to say, this embodiment can be combined with the above-described embodiment.
１…ポンプ本体(ポンプボディ)，２…プランジャ，４…ばね，６…シリンダ，８…吐出弁，９…ダンパ，１０…ダンパ室，１４…ダンパカバー，１４１…ダンパ保持部材３０…吸入弁，１００…リリーフ弁機構，１０１…フランジ DESCRIPTION OF SYMBOLS 1 ... Pump main body (pump body), 2 ... Plunger, 4 ... Spring, 6 ... Cylinder, 8 ... Discharge valve, 9 ... Damper, 10 ... Damper chamber, 14 ... Damper cover, 141 ... Damper holding member 30 ... Suction valve, 100 ... relief valve mechanism, 101 ... flange
Claims (5)
前記ダンパカバーは凸部を有し、前記ダンパと前記ダンパカバーとの間にダンパ保持部材を備え、
前記ダンパ保持部材が、前記ダンパカバーの凸部の内側面と複数点または面で接触し、かつ前記ダンパカバーの凸部の上面と側面に接触し、
前記ダンパ保持部材の前記ダンパカバーと接触しない部分は、円形で断面が波型形状の部材であることを特徴とする高圧燃料供給ポンプ。 A high-pressure fuel supply pump having a damper and a damper cover,
The damper cover has a convex portion, and includes a damper holding member between the damper and the damper cover,
The damper holding member comes into contact with the inner surface and the plurality of points or surfaces of the convex portion of the damper cover and contacts the top surface and the side surface of the protrusion of the damper cover,
A portion of the damper holding member that does not contact the damper cover is a member having a circular shape and a corrugated cross section .
前記ダンパカバーに外側に突出する凸部を有し，前記ダンパカバーと前記ダンパとの間にダンパ保持部材を備え，
前記ダンパ保持部材が、前記ダンパカバーの凸部の内側面と複数点または面で接触し、かつ前記ダンパカバーの凸部の上面と側面に接触し、
前記ダンパ保持部材の前記ダンパカバーと接触しない部分は、円形で断面が波型形状の部材であることを特徴とする高圧燃料供給ポンプ。 A plunger that round trip movement, ejects the compression chamber of the fuel which changes volume by the reciprocating motion of the plunger, the the compression chamber intake valve for supplying fuel to the fuel pressurized from the pressure chamber A discharge valve; a pump body having the pressurizing chamber; the plunger, the suction valve, and the discharge valve are assembled; a damper disposed in a damper chamber formed in the pump body; and the damper chamber High pressure fuel supply pump with a damper cover covering
The damper cover has a protrusion protruding outward, and includes a damper holding member between the damper cover and the damper.
The damper holding member is in contact with the inner surface of the convex portion of the damper cover at a plurality of points or surfaces, and is in contact with the upper surface and the side surface of the convex portion of the damper cover;
A portion of the damper holding member that does not contact the damper cover is a member having a circular shape and a corrugated cross section .
前記ダンパカバーと前記ダンパ保持部材が前記ダンパカバーの凸部の軸方向と径方向で接触することを特徴とする高圧燃料供給ポンプ。 The high-pressure fuel supply pump according to claim 1 or 2 ,
The high-pressure fuel supply pump, wherein the damper cover and the damper holding member are in contact with each other in an axial direction and a radial direction of a convex portion of the damper cover.
前記凸部は、前記ダンパカバーに外側に突出する概略円形状であることを特徴する高圧燃料供給ポンプ。 The high-pressure fuel supply pump according to claim 1 or 2 ,
The convex portion, the high-pressure fuel supply pump for being a generally circular shape protruding outwardly in the damper cover.
前記ダンパカバーと前記ダンパ保持部材の接続方法をカシメもしくははめあいにて実施することを特徴とする高圧燃料供給ポンプ。 The high-pressure fuel supply pump according to any one of claims 1 to 4 ,
A high-pressure fuel supply pump, wherein the damper cover and the damper holding member are connected by caulking or fitting.
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| JP6920543B2 (en) * | 2018-04-06 | 2021-08-18 | 日立Astemo株式会社 | High pressure fuel supply pump |
| KR20200140902A (en) * | 2018-05-25 | 2020-12-16 | 이구루코교 가부시기가이샤 | Damper device |
| DE102018212229A1 (en) * | 2018-07-23 | 2020-01-23 | Continental Automotive Gmbh | Pump for a motor vehicle, holding device, assembly and method |
| JP2020045849A (en) * | 2018-09-20 | 2020-03-26 | 株式会社不二工機 | Pulsation damper |
| JP7126696B2 (en) * | 2018-09-20 | 2022-08-29 | 株式会社不二工機 | pulsation damper |
| US11408386B2 (en) | 2018-10-01 | 2022-08-09 | Hitachi Astemo, Ltd. | High-pressure fuel pump |
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| JP2012251467A (en) * | 2011-06-02 | 2012-12-20 | Hitachi Automotive Systems Ltd | Fuel pressure pulsation reducing mechanism and high-pressure fuel supply pump of internal combustion engine equipped with the same |
| JP2013060945A (en) * | 2011-08-23 | 2013-04-04 | Denso Corp | High pressure pump |
| JP6066483B2 (en) * | 2013-03-26 | 2017-01-25 | マルヤス工業株式会社 | Fuel pressure pulsation reduction device |
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| KR102417695B1 (en) * | 2020-11-10 | 2022-07-07 | 주식회사 현대케피코 | Damper spring structure for reducing radiation noise of high pressure fuel pump |
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