JPS6145073B2 - - Google Patents
Info
- Publication number
- JPS6145073B2 JPS6145073B2 JP56055909A JP5590981A JPS6145073B2 JP S6145073 B2 JPS6145073 B2 JP S6145073B2 JP 56055909 A JP56055909 A JP 56055909A JP 5590981 A JP5590981 A JP 5590981A JP S6145073 B2 JPS6145073 B2 JP S6145073B2
- Authority
- JP
- Japan
- Prior art keywords
- pressure port
- opening
- hole
- piston
- piston chamber
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
Links
- 239000003921 oil Substances 0.000 description 45
- 230000003628 erosive effect Effects 0.000 description 13
- 239000012530 fluid Substances 0.000 description 10
- 230000008859 change Effects 0.000 description 8
- 238000005461 lubrication Methods 0.000 description 7
- 239000002184 metal Substances 0.000 description 3
- 229910052751 metal Inorganic materials 0.000 description 3
- 230000009471 action Effects 0.000 description 2
- 230000009467 reduction Effects 0.000 description 2
- 229910000881 Cu alloy Inorganic materials 0.000 description 1
- 230000008901 benefit Effects 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000005755 formation reaction Methods 0.000 description 1
- 230000005484 gravity Effects 0.000 description 1
- 230000001771 impaired effect Effects 0.000 description 1
- 238000002347 injection Methods 0.000 description 1
- 239000007924 injection Substances 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 239000002480 mineral oil Substances 0.000 description 1
- 235000010446 mineral oil Nutrition 0.000 description 1
- 230000000737 periodic effect Effects 0.000 description 1
- 238000006116 polymerization reaction Methods 0.000 description 1
- 230000002265 prevention Effects 0.000 description 1
- 238000005086 pumping Methods 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
- 230000001360 synchronised effect Effects 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
- F04B1/2014—Details or component parts
- F04B1/2042—Valves
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Reciprocating Pumps (AREA)
Description
【発明の詳細な説明】 本発明はピストンポンプの改良に関する。[Detailed description of the invention] The present invention relates to improvements in piston pumps.
第１図および第２図はこの種のピストンポンプ
の一例を示す。このポンプは、駆動軸１、駆動軸
１にスプライン連結され且つ駆動軸１の回りに駆
動軸と平行に複数個のピストン室２を形成するシ
リンダブロツク３、ピストン室２に嵌挿されたピ
ストン４の行程を規制する斜板５、バルブブロツ
ク６に固定され且つシリンダブロツク３と接する
弁板７、ハウジング８等で構成されている。 1 and 2 show an example of this type of piston pump. This pump includes a drive shaft 1, a cylinder block 3 connected to the drive shaft 1 by splines and forming a plurality of piston chambers 2 around the drive shaft 1 in parallel with the drive shaft, and a piston 4 fitted into the piston chambers 2. The valve plate 7 is fixed to the valve block 6 and is in contact with the cylinder block 3, a housing 8, etc.
シリンダブロツク３は、駆動軸１との間に介装
されたばね９により弁板７に押し当てられ、駆動
軸１にて駆動される。このシリンダブロツク３の
回転によりピストン４は駆動軸上を公転しながら
斜板５の傾斜角αで規制された行程を往復運動
し、弁板７の流体吸入用の低圧口１０と流体吐出
用の高圧口１１を介してポンプ作用を行う。 The cylinder block 3 is pressed against the valve plate 7 by a spring 9 interposed between the cylinder block 3 and the drive shaft 1, and is driven by the drive shaft 1. Due to this rotation of the cylinder block 3, the piston 4 revolves on the drive shaft and reciprocates through a stroke regulated by the inclination angle α of the swash plate 5. Pumping action is performed via the high pressure port 11.
弁板７は、第２図に示す如く、シリンダブロツ
ク３に対向する面に円弧状の低圧口１０と高圧口
１１を形成している。ピストン室２につながる開
口１２は、低圧口１０と高圧口１１のピツチ円１
３上にあつて、シリンダブロツク３が回転する
と、低圧口１０と高圧口１１に交互に連通し、ピ
ストン室２内の圧力は、ピストン４が吸入行程に
ある時には略低圧口１０の圧力を一致し、吐出行
程にある時には略高圧口１１の圧力と一致する。
ピストン４が吸込行程を終えて吐出行程に移ろう
とするとき、則ち、開口１２が低圧口１０を出て
高圧口１１の手前に達するときには、開口１２は
低圧口１０と高圧口１１のいずれとも遮断ないし
略遮断された状態にあり、ピストン室２の圧力が
略低圧口１０の圧力から略高圧口１１の圧力に遷
移する行程、いわゆる昇圧の圧力切換行程〔以
下、昇圧行程という〕にある。逆に、ピストン４
が吐出行程から吸入行程に移ろうとするときの開
口１２は、降圧の圧力切換行程〔以下、降圧行程
という〕にある。 As shown in FIG. 2, the valve plate 7 has an arc-shaped low pressure port 10 and a high pressure port 11 formed on the surface facing the cylinder block 3. The opening 12 connected to the piston chamber 2 has a pitch circle 1 between the low pressure port 10 and the high pressure port 11.
3, when the cylinder block 3 rotates, it communicates alternately with the low pressure port 10 and the high pressure port 11, and the pressure in the piston chamber 2 is approximately equal to the pressure in the low pressure port 10 when the piston 4 is in the suction stroke. Therefore, during the discharge stroke, the pressure substantially matches the pressure of the high pressure port 11.
When the piston 4 finishes the suction stroke and is about to move on to the discharge stroke, that is, when the opening 12 leaves the low pressure port 10 and reaches before the high pressure port 11, the opening 12 is connected to both the low pressure port 10 and the high pressure port 11. It is in a shut-off or substantially shut-off state, and is in a step in which the pressure in the piston chamber 2 transitions from the pressure in the low-pressure port 10 to the pressure in the high-pressure port 11, a so-called pressure-up pressure switching step (hereinafter referred to as a pressure-up step). Conversely, piston 4
When the opening 12 is about to move from the discharge stroke to the suction stroke, the opening 12 is in the pressure-reducing pressure switching stroke (hereinafter referred to as the pressure-reducing stroke).
昇圧行程では開口１２が高圧口１１に連通する
瞬間にピストン室２の圧力が急激に上昇し、降圧
行程では開口１２が低圧口１０に連通する瞬間に
ピストン室２の圧力が急激に低下する。この昇・
降圧行程における瞬間的な圧力変化は、ポンプ内
部にシリンダブロツク３の回転に同調した周期的
な衝撃力を生ぜしめ、これがピストンポンプの騒
音、振動発生の主原因となつていた。 In the pressure increasing stroke, the pressure in the piston chamber 2 rapidly increases at the moment the opening 12 communicates with the high pressure port 11, and in the pressure decreasing stroke, the pressure in the piston chamber 2 rapidly decreases at the moment the opening 12 communicates with the low pressure port 10. This noboru・
The instantaneous pressure change during the pressure reduction stroke generates a periodic impact force within the pump that is synchronized with the rotation of the cylinder block 3, and this is the main cause of noise and vibration in the piston pump.
そこで、従来ではピストンポンプの騒音や振動
を低減する目的で前述の昇・降圧行程におけるピ
ストン室２内の圧力変化をゆるやかにするための
工夫がなされている。即ち、低・高圧口の圧力差
を変化時間で除した値である圧力変化率を小さく
するために、第３図および第４図に示すように高
圧口１１に連通する切欠溝１４と低圧口１０に連
通する切欠溝１４を設けるか、または第５図およ
び第６図に示すようにバルブブロツク対向面に形
成した油溝１５を介して高圧口１１に連通する主
導油孔１６と油溝１７を介して低圧口１０に連通
する主導油孔１６を設けるものであり、昇圧行程
では切欠溝１４または主導油孔１６の絞り作用で
高圧口１１の流体が徐々に開口１２を介してピス
トン室２内に流入することにより、昇圧の圧力変
化率が小さくなり、前述の衝撃力が緩和される。
降圧行程でも同様にして衝撃力が緩和されること
になる。この対策は騒音や振動の低減に大いに役
立ち、ピストンポンプに普及している。 Therefore, in the past, in order to reduce the noise and vibration of the piston pump, efforts have been made to make the pressure change in the piston chamber 2 more gradual during the above-mentioned pressure raising and lowering strokes. That is, in order to reduce the pressure change rate, which is the value obtained by dividing the pressure difference between the low and high pressure ports by the change time, the notched groove 14 communicating with the high pressure port 11 and the low pressure port are connected as shown in FIGS. 3 and 4. A main oil hole 16 and an oil groove 17 that communicate with the high pressure port 11 through a notch groove 14 communicating with the valve block 10 or an oil groove 15 formed on the opposing surface of the valve block as shown in FIGS. 5 and 6. A main oil hole 16 is provided which communicates with the low pressure port 10 through the pressure increase stroke, and the fluid in the high pressure port 11 gradually flows through the opening 12 into the piston chamber 2 due to the throttling action of the notch groove 14 or the main oil hole 16. By flowing into the interior, the rate of pressure change due to pressurization becomes small, and the above-mentioned impact force is alleviated.
The impact force will be alleviated in the same way during the pressure-reducing stroke. This measure greatly helps reduce noise and vibration, and is widely used in piston pumps.
ところで、昇圧行程において、第７図および第
９図に示すように、ピストン室２の開口１２が切
欠溝１４ないし主導油孔１６と連通する瞬間は、
ピストン室２と高圧口１１との圧力差が大きいた
め、切欠溝１４ないし主導油孔１６からの流体が
矢印方向に噴流状態で開口１２へ流入する。鉱物
油を用いた実験によれば、圧力差が200Kgf/cm2に
おいて噴流の平均流速は200m/sであつた。この
ような高速の流体が開口１２ないしピストン室２
の壁面に衝突すると、金属表面のキヤビテーシヨ
ンエロージヨン〔以下、壊食という〕が発生す
る。キヤビテーシヨンの強度および金属表面の壊
食の度合は、絞りの前後の圧力差、流体の粘度お
よび比重、流体中への空気の混合率、開口１２の
低圧口側壁面と絞りとの距離および低圧側自体の
圧力等に依存するが、特に圧力差の影響を強く受
け、圧力差の増大に対し壊食の度合いは幾何級数
的に増大する。従つて、ピストンポンプがその特
徴を生かすべくより高圧領域で使用されるように
なると、開口１２ないしピストン室２の壊食の影
響が無視できなくなり、これがピストンポンプの
使用限界圧力の上限を制限する大きな原因となつ
ている。 By the way, in the pressure increase stroke, as shown in FIGS. 7 and 9, at the moment when the opening 12 of the piston chamber 2 communicates with the notch groove 14 or the main oil hole 16,
Since the pressure difference between the piston chamber 2 and the high pressure port 11 is large, the fluid from the notch groove 14 or the main oil hole 16 flows into the opening 12 in a jet state in the direction of the arrow. According to an experiment using mineral oil, the average flow velocity of the jet was 200 m/s at a pressure difference of 200 Kgf/cm 2 . Such high-speed fluid flows through the opening 12 or the piston chamber 2.
When the metal collides with the wall, cavitation erosion (hereinafter referred to as erosion) occurs on the metal surface. The strength of cavitation and the degree of erosion on the metal surface are determined by the pressure difference before and after the throttle, the viscosity and specific gravity of the fluid, the mixing ratio of air into the fluid, the distance between the low-pressure port side wall of the opening 12 and the throttle, and the low-pressure side. Although it depends on its own pressure, etc., it is particularly strongly influenced by the pressure difference, and the degree of erosion increases exponentially as the pressure difference increases. Therefore, as piston pumps come to be used in higher pressure areas to take advantage of their characteristics, the influence of erosion of the opening 12 or the piston chamber 2 cannot be ignored, and this limits the upper limit of the working pressure of the piston pump. This is a major cause.
発明者等の実験結果によれば、第１１図に示す
ように昇圧行程で開口１２と主導油孔１６が連通
する直前の状態、即ち、シリンダブロツク３と弁
板７間に形成された油膜厚さΔｈおよび微小の正
重合量Δｘとが存在する状態においては、主導油
孔１６′からの主噴流１８は、すきまΔｈにより
方向ずけられて弁板７の摺動面１９と略平行に噴
出して開口１２の低圧口側に衝突し、開口１２の
低圧口側角部２０や弁板７の低圧口側角部２１に
著しい壊食をひき起こす。ところで、シリンダブ
ロツク３は弁板７を境界潤滑状態で高速周動する
ため、通常いずれかの表面に銅合金を始めとする
比較的硬度の低い摺動材料を用いているが、この
摺動材料表面の壊食が特に著しく、また弁板７も
表面硬度が低い場合には前述と同様の壊食が発生
し、ポンプ効率、特に容積効率が著しく劣化す
る。なお、シリンダブロツク３と弁板７間に形成
されたすきまΔｈに示すより方向づけられた噴流
１８は、第１３図に示すような開口１２の端部お
よび主導油孔１６の端部を面取り２４するような
マクロ的な形成によつて方向を変えることが困難
なことが実験で確認されている。 According to the experimental results of the inventors, as shown in FIG. 11, the thickness of the oil film formed between the cylinder block 3 and the valve plate 7 is the state immediately before the opening 12 and the main oil hole 16 communicate with each other during the pressure increase stroke. When the gap Δh and the small amount of positive polymerization Δx exist, the main jet flow 18 from the main oil hole 16' is directed by the gap Δh and is ejected approximately parallel to the sliding surface 19 of the valve plate 7. and collides with the low-pressure port side of the opening 12, causing significant erosion to the low-pressure port side corner 20 of the opening 12 and the low-pressure port side corner 21 of the valve plate 7. By the way, since the cylinder block 3 rotates around the valve plate 7 at high speed in a state of boundary lubrication, a relatively low-hardness sliding material such as a copper alloy is normally used on one of the surfaces. If the surface erosion is particularly severe and the valve plate 7 also has a low surface hardness, the same erosion as described above will occur, and the pump efficiency, especially the volumetric efficiency, will be significantly degraded. Incidentally, the jet flow 18, which is oriented as shown by the gap Δh formed between the cylinder block 3 and the valve plate 7, chamfers 24 the end of the opening 12 and the end of the main oil hole 16 as shown in FIG. Experiments have confirmed that it is difficult to change the direction due to such macroscopic formations.
本発明は、前記の点に鑑み検討の結果なされた
もので、従来の弁板に小孔を付加する程度の簡潔
な構成により、ポンプ効率を低下させることなし
に前述の壊食現象を解消することに成功したもの
である。 The present invention has been made as a result of studies in view of the above points, and uses a simple structure that involves adding small holes to a conventional valve plate, thereby eliminating the above-mentioned erosion phenomenon without reducing pump efficiency. It was extremely successful.
以下本発明の実施例を図面について説明する。
第１４図に示すものは、弁板７の低圧口１０と高
圧口１１間に、高圧口１１に油溝１５を介して連
通する主導油孔１６よりも先にピストン室２の開
口１２と連通させる副導油孔２２を穿設してこれ
を油溝１５と連通すると共に、低圧口１０に油溝
１７を介して連通する主導油孔１６よりも先にピ
ストン室２の開口１２と連通させる副導油孔２２
を穿設してこれを油溝１７の連通するものであ
る。第１５図に示すものは、弁板７の低圧口１０
と高圧口１１間に、高圧口１１に通じる切欠溝１
４よりも先にピストン室２の開口１２と連通させ
る副導油孔２２を穿設してこれを油溝１５により
高圧口１１に連通すると共に、低圧口１０に通じ
る切欠溝１４よりも先に開口１２と連通させる副
導油孔２２を穿設してれを油溝１７により低圧口
１０に連通するものである。第１４図および第１
５図において副導油孔２２が降圧側にも設けられ
ているには、ポンプが両傾転使用の場合、弁板７
の高・低圧口が入れかわるためであり、片傾転使
用で高・低圧口が固定している場合は昇圧側のみ
に設ければよい。 Embodiments of the present invention will be described below with reference to the drawings.
The one shown in FIG. 14 communicates between the low pressure port 10 and high pressure port 11 of the valve plate 7 with the opening 12 of the piston chamber 2 before the main oil hole 16 communicates with the high pressure port 11 via the oil groove 15. A sub oil guide hole 22 is drilled to communicate with the oil groove 15, and is also communicated with the opening 12 of the piston chamber 2 before the main oil hole 16, which communicates with the low pressure port 10 via the oil groove 17. Sub oil guide hole 22
is bored and communicated with the oil groove 17. What is shown in FIG. 15 is the low pressure port 10 of the valve plate 7.
A cutout groove 1 communicating with the high pressure port 11 is provided between the high pressure port 11 and the high pressure port 11.
A sub-lubrication hole 22 is bored to communicate with the opening 12 of the piston chamber 2 before the opening 12 of the piston chamber 2, and this is communicated with the high-pressure port 11 through the oil groove 15, and also before the notch groove 14 that communicates with the low-pressure port 10. A sub oil guide hole 22 is bored to communicate with the opening 12, and the sub oil guide hole 22 is communicated with the low pressure port 10 through an oil groove 17. Figure 14 and 1
In Fig. 5, the sub-lubrication hole 22 is also provided on the pressure-reducing side.
This is because the high and low pressure ports of the pump are switched, and if the high and low pressure ports are fixed when using a single tilt rotation, it is only necessary to provide them on the boost side.
なお、副導油孔２２の直径は主導油孔１６の数
分の１と小さく、また、副導油孔２２が開口１２
に開口した直後に主導油孔１６から流体が噴出す
るように副導油孔２２と主導油孔１６〔または切
欠溝１４〕間の間隔を選定している。 The diameter of the sub oil guide hole 22 is as small as a fraction of the main oil hole 16, and the sub oil guide hole 22 is smaller than the opening 12.
The interval between the auxiliary oil guide hole 22 and the main oil hole 16 (or the notched groove 14) is selected so that fluid is ejected from the main oil hole 16 immediately after the main oil hole 16 opens.
本実施例は前記するような構成であるから、第
１６図に示すようにピストン室２の開口１２が一
部低圧口１０から脱し副導油孔２２からの副噴流
２３が弁板７の摺動面１９に沿つて噴射し始める
状態では主導油孔１６からは流体の噴書はない。
副導油孔２２が開口１２に開口すると、第１８図
に示すように主導油孔１６から主噴流１８が摺動
面１９に沿つて噴出し始め、この主噴流１８は副
導油孔２２から噴出するピストン４軸線と略平行
な副噴流２３により噴出角θが大となる方向へ大
きく方向変換せしめられる。これにより主噴流１
８はピストン室２ないしピストン４内壁との衝突
位置までの距離が長くなる。従つて、噴流による
壊食の発生を防ぐことができる。なお、主噴流１
８がピストン室２ないしピストン４内壁の壁面硬
度の高い部位に当たるように副導油孔２２の穿設
方向や大きさ等を設定するようにしてもよい。第
１９図は切欠溝１４からの主噴流１８が噴導油孔
２２からの副噴流２３により噴出角θが大となる
方向へ大きく方向変換せしめられた状態を示す。 Since this embodiment has the above-mentioned configuration, the opening 12 of the piston chamber 2 partially escapes from the low-pressure port 10, and the sub-jet 23 from the sub-lubrication hole 22 flows through the valve plate 7. When the fluid starts to be jetted along the moving surface 19, there is no jet of fluid from the main oil hole 16.
When the sub oil guide hole 22 opens into the opening 12, the main jet 18 starts to jet from the main oil guide hole 16 along the sliding surface 19 as shown in FIG. The sub-jet flow 23, which is substantially parallel to the 4-axis axis of the ejecting piston, causes the direction to change significantly in the direction in which the ejection angle θ becomes large. As a result, the main jet 1
8, the distance from the piston chamber 2 to the collision position with the inner wall of the piston 4 is longer. Therefore, it is possible to prevent erosion caused by the jet flow. In addition, the main jet 1
The direction, size, etc. of the auxiliary oil guide hole 22 may be set so that the hole 8 hits a portion of the inner wall of the piston chamber 2 or the piston 4 that has a high wall surface hardness. FIG. 19 shows a state in which the direction of the main jet 18 from the notched groove 14 is greatly changed by the auxiliary jet 23 from the jet oil hole 22 in a direction in which the jet angle θ becomes large.
実験によれば、容量がおよそ100c.c./revのピス
トンポンプで主導油孔１６の直径が１〜２mmで
は、副導油孔２２は0.5mm位で十分に主噴流の方
向制御が可能であり、シリンダブロツク３、弁板
７の表面の壊食現象を防止できること、そして、
これはポンプ吐出圧力が400Kgf/cm2の高圧であつ
ても有効であることが判明した。また、副導油孔
２２からの摺動面に沿う副噴流２３は、第１７図
に示すように噴流の長さＳ＋Δｘおよび幅Ｗとも
小さく、これによる壊食現象は無視できること、
さらに、副導油孔２２は直径が小さいので、ポン
プ効率特に容積効率の低減率は十分に小さく、そ
の影響は無視できる程度のものであることが確認
されている。 According to experiments, when the diameter of the main oil hole 16 is 1 to 2 mm in a piston pump with a capacity of about 100 c.c./rev, the direction of the main jet flow can be sufficiently controlled with the auxiliary oil guide hole 22 of about 0.5 mm. Yes, it is possible to prevent erosion of the surfaces of the cylinder block 3 and valve plate 7, and
This was found to be effective even when the pump discharge pressure was as high as 400 Kgf/cm 2 . Furthermore, the length S+Δx and width W of the sub-jet 23 along the sliding surface from the sub-lubrication hole 22 are small, as shown in FIG. 17, and the erosion phenomenon caused by this can be ignored;
Furthermore, since the diameter of the sub-lubrication hole 22 is small, the rate of reduction in pump efficiency, particularly volumetric efficiency, is sufficiently small, and it has been confirmed that the effect thereof is negligible.
なお、ピストン室２の開口１２には、第２０図
に示すような斜孔としたものがあるが、この場合
には、第２１図に示すように主導油孔１６および
副導油孔２２を低圧口１０、高圧口１１のピツチ
円１３から外すなどして噴流１８が斜孔の開口壁
面に衝突しないようにする必要がある。 Note that the opening 12 of the piston chamber 2 may have an oblique hole as shown in FIG. It is necessary to prevent the jet stream 18 from colliding with the opening wall surface of the diagonal hole by removing it from the pitch circle 13 of the low pressure port 10 and high pressure port 11.
以上説明したように本発明においては、弁板に
ポンプ騒音等の低減対策用の主導油孔ないし切欠
溝からの主噴流の噴射角を大きく変え得る副導油
孔を形成したから、従来の弁板に小孔を付加する
程度の簡潔な構成によつて壊食現象の発生を防止
することができ、ポンプをより高圧領域で使用で
きると共に、ポンプの耐久性、信頼性を高め得
る。また、既存の弁板にも簡単に適用でき、しか
も副導油孔は直径が小さいので、ポンプ効率を損
うことがない。 As explained above, in the present invention, the sub-lubrication hole is formed in the valve plate to greatly change the injection angle of the main jet flow from the main oil hole or notched groove for reducing pump noise, etc. A simple configuration of adding small holes to the plate can prevent the occurrence of erosion phenomena, allow the pump to be used in a higher pressure region, and improve the durability and reliability of the pump. In addition, it can be easily applied to existing valve plates, and since the auxiliary oil guide hole has a small diameter, pump efficiency will not be impaired.
なお、前述の図面および記載は、主にピストン
ポンプについてであつたが、ピストンモータでは
低圧口は流体吐出側に高圧口が流体吸入側となつ
て作動することになる。 Although the above-mentioned drawings and descriptions mainly refer to a piston pump, a piston motor operates with the low pressure port on the fluid discharge side and the high pressure port on the fluid suction side.
第１図はアキシアルピストンポンプの一部縦断
面図、第２図は第１図のＡ−Ａ線矢視図、第３図
および第５図はそれぞれ騒音防止対策を施した弁
板の正面図、第４図は第３図のＢ−Ｂ線断面図、
第６図は第５図のＣ−Ｃ線断面図、第７図および
第９図はそれぞれ昇圧行程時の主噴流噴出方向を
示す平面図、第８図は第７図のＤ−Ｄ線断面図、
第１０図は第９図のＥ−Ｅ線断面図、第１１図は
昇圧行程時主導油孔からの主噴流の噴出状態を示
す断面図、第１２図は昇圧行程時切欠溝からの主
噴流の噴出状態を示す断面図、第１３図は昇圧行
程時面取りした切欠溝からの主噴流の噴出状態を
示す断面図、第１４図は本発明の一実施例である
弁板部分の平面図、第１５図は本発明のいま一つ
の実施例である弁板部分の平面図、第１６図は副
導油孔からの副噴流の噴出状態を示す縦断面図、
第１７図は第１６図に示す副噴流の平面図、第１
８図および第１９図はそれぞれ副噴流による主噴
流噴出方向変換状態を示す縦断面図、第２０図は
アキシアルピストンポンプのピストン室の開口付
近の一例を示す一部切欠縦断面図、第２１図は第
２０図の傾斜開口に対する主・副導油孔の配置例
図である。
１……駆動軸、２……ピストン室、３……シリ
ンダブロツク、４……ピストン、５……斜板、６
……バルブブロツク、７……弁板、１０……低圧
口、１１……高圧口、１２……開口、１４……切
欠溝、１５，１７……油溝、１６……主導油孔、
１８……主噴流、２２……副導油孔、２３……副
噴流。
Figure 1 is a partial vertical sectional view of the axial piston pump, Figure 2 is a view taken along the line A-A in Figure 1, and Figures 3 and 5 are front views of the valve plate with noise prevention measures taken respectively. , FIG. 4 is a sectional view taken along line B-B in FIG. 3,
6 is a sectional view taken along the line C-C in FIG. 5, FIGS. 7 and 9 are plan views showing the main jet ejection direction during the boost stroke, and FIG. 8 is a sectional view taken along the line D-D in FIG. 7. figure,
Fig. 10 is a sectional view taken along the line E-E in Fig. 9, Fig. 11 is a sectional view showing the jetting state of the main jet from the main oil hole during the boost stroke, and Fig. 12 is the main jet from the notch during the boost stroke. FIG. 13 is a cross-sectional view showing the jetting state of the main jet flow from the chamfered notch groove during the boost stroke; FIG. 14 is a plan view of the valve plate portion according to an embodiment of the present invention; FIG. 15 is a plan view of a valve plate portion according to another embodiment of the present invention, and FIG. 16 is a longitudinal cross-sectional view showing the state of the sub-jet ejected from the sub-oil guide hole.
Figure 17 is a plan view of the secondary jet shown in Figure 16;
8 and 19 are longitudinal cross-sectional views showing a state in which the main jet ejecting direction is changed by the sub-jet, respectively. FIG. 20 is a partially cutaway longitudinal cross-sectional view showing an example of the vicinity of the opening of the piston chamber of an axial piston pump. 20 is a diagram illustrating an example of the arrangement of main and auxiliary oil guide holes for the inclined opening in FIG. 20. 1... Drive shaft, 2... Piston chamber, 3... Cylinder block, 4... Piston, 5... Swash plate, 6
... Valve block, 7 ... Valve plate, 10 ... Low pressure port, 11 ... High pressure port, 12 ... Opening, 14 ... Notch groove, 15, 17 ... Oil groove, 16 ... Main oil hole,
18...Main jet, 22...Sub oil guide hole, 23...Sub jet.
Claims (1)
り低圧のピストン室の開口を主導油孔ないし切欠
溝を介して高圧口に連通するようにしたものにお
いて、弁板に主導油孔ないし切欠溝より先にピス
トン室の開口に通じる副導油孔を設け、この副導
油孔は主導油孔より小径で高圧口に連通すると共
に、その副噴流により主導油孔ないし切欠溝の先
端がピストン室に開口する直前に生じる主噴流が
ピストン室の奥部の方へ向きを変えるように副導
油孔の開口の位置と向きを定めたことを特徴とす
るピストンポンプ。1 In a device in which the opening of a piston chamber with a lower pressure than the high pressure port located between the low pressure port and the high pressure port of the valve plate is communicated with the high pressure port via the main oil hole or notched groove, there is a main oil hole in the valve plate. A sub oil guide hole that communicates with the opening of the piston chamber is provided before the main oil hole or the notch groove, and this sub oil guide hole has a smaller diameter than the main oil hole and communicates with the high pressure port, and the tip of the main oil hole or the notch groove is A piston pump characterized in that the position and direction of the opening of the auxiliary oil guide hole are determined so that the main jet flow generated immediately before the auxiliary oil guide hole opens into the piston chamber changes its direction toward the inner part of the piston chamber.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP56055909A JPS57171086A (en) | 1981-04-13 | 1981-04-13 | Piston pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP56055909A JPS57171086A (en) | 1981-04-13 | 1981-04-13 | Piston pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS57171086A JPS57171086A (en) | 1982-10-21 |
| JPS6145073B2 true JPS6145073B2 (en) | 1986-10-06 |
Family
ID=13012232
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP56055909A Granted JPS57171086A (en) | 1981-04-13 | 1981-04-13 | Piston pump |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS57171086A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS61118572U (en) * | 1985-01-09 | 1986-07-26 |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4550645A (en) * | 1984-04-27 | 1985-11-05 | Sundstrand Corporation | Thin valve plate for a hydraulic unit |
| JP2578119Y2 (en) * | 1991-07-31 | 1998-08-06 | 川崎重工業株式会社 | Hydraulic motor |
| KR980009921A (en) * | 1996-07-31 | 1998-04-30 | 김무 | Valve Plate Structure of Axial Piston Pump |
| JP4657520B2 (en) * | 2001-08-22 | 2011-03-23 | 東芝機械株式会社 | Piston pump / motor |
| CN102434420A (en) * | 2012-01-13 | 2012-05-02 | 无锡威孚精密机械制造有限责任公司 | Gas etching preventing distribution disk |
| JP2023042733A (en) | 2021-09-15 | 2023-03-28 | ナブテスコ株式会社 | Fluid machine and construction machine |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS51129905A (en) * | 1975-04-24 | 1976-11-11 | Lucas Industries Ltd | Hydraulic rotary machines |
-
1981
- 1981-04-13 JP JP56055909A patent/JPS57171086A/en active Granted
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS51129905A (en) * | 1975-04-24 | 1976-11-11 | Lucas Industries Ltd | Hydraulic rotary machines |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS61118572U (en) * | 1985-01-09 | 1986-07-26 |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS57171086A (en) | 1982-10-21 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN100447410C (en) | Axial piston hydraulic pump motor | |
| JPS6145073B2 (en) | ||
| JP4884135B2 (en) | Hydraulic rotating machine | |
| US5230274A (en) | Variable displacement hydraulic pump with quiet timing | |
| JPH05504103A (en) | axial bearing | |
| JP4657520B2 (en) | Piston pump / motor | |
| KR101772734B1 (en) | Pulsation swash plate type piston pump having the function of preventing | |
| CN114294193A (en) | Hydrostatic axial piston machine | |
| CN110094316B (en) | Hydraulic press | |
| JP2578119Y2 (en) | Hydraulic motor | |
| JPS597786A (en) | Piston-type fluid machine | |
| KR20130065996A (en) | Valve plate | |
| JPS6045314B2 (en) | piston pump | |
| JP2000345955A (en) | Piston pump/motor | |
| KR19980069663A (en) | Valve plate | |
| KR19980067343A (en) | Valve plate | |
| KR19980079198A (en) | Hydraulic piston pump | |
| JPH0578977U (en) | Piston pump | |
| KR200203910Y1 (en) | Axial piston type hydraulic pump and hydraulic motor | |
| US6893231B2 (en) | Hydraulic device | |
| US7090472B2 (en) | Pump or motor with interconnected chambers in the rotor | |
| KR20150115042A (en) | Valve plate for piston type hydraulic motor | |
| KR980009921A (en) | Valve Plate Structure of Axial Piston Pump | |
| KR100674656B1 (en) | Inclined Board Structure for Oil Hydraulic Pump | |
| JP2000080976A (en) | Piston pump |