JPH0510514B2 - - Google Patents
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- Publication number
- JPH0510514B2 JPH0510514B2 JP58081149A JP8114983A JPH0510514B2 JP H0510514 B2 JPH0510514 B2 JP H0510514B2 JP 58081149 A JP58081149 A JP 58081149A JP 8114983 A JP8114983 A JP 8114983A JP H0510514 B2 JPH0510514 B2 JP H0510514B2
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- Japan
- Prior art keywords
- gear
- tooth
- contact point
- continuous contact
- pitch circle
- 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.)
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- 239000012530 fluid Substances 0.000 claims description 2
- 238000010586 diagram Methods 0.000 description 8
- 238000004519 manufacturing process Methods 0.000 description 1
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- Rotary Pumps (AREA)
Description
【発明の詳細な説明】
本発明は、一対の連続接触歯車を回転子とし、
無脈動でしかも歯車の接触歯面が無負荷であるよ
うにした歯車ポンプに関する。DETAILED DESCRIPTION OF THE INVENTION The present invention comprises a pair of continuous contact gears as a rotor,
This invention relates to a gear pump that is pulsation-free and has no load on the contact tooth surface of the gear.
従来の歯車ポンプのほとんどのものは、一対の
歯車が同形、同大であり製作上は非常に有利であ
るが、従動車に吐出し圧力による回転トルク即ち
歯面力が発生する欠点がある。 Most conventional gear pumps have a pair of gears of the same shape and size, which is very advantageous in manufacturing, but has the disadvantage that rotational torque, ie tooth surface force, is generated in the driven wheel due to discharge pressure.
本発明は叙上の点に着目して成されたもので、
以下にその理論的根拠を説明する。歯数Z1、Z2の
一対の歯車O1、O2がdθ1、dθ2だけ回転したとき
dQだけの容積を吐出したものとすると、一対の
歯車を回転させるに要したエネルギーはdQの流
体にＰの圧力を与えるために消費されるものであ
るから次式が成立する。 The present invention has been made by focusing on the above points,
The rationale is explained below. When a pair of gears O 1 and O 2 with number of teeth Z 1 and Z 2 rotate by dθ 1 and dθ 2
Assuming that a volume of dQ is discharged, the energy required to rotate the pair of gears is consumed to apply a pressure of P to the fluid of dQ, so the following equation holds true.
PdQ＝T1dθ1＋T2dθ2 ……(1)
∴dQ／dθ1＝１／Ｐ（T1＋Z1／Z2T2） ……(2)
（ただし、T1：歯車O1の回転トルク、T2：歯
車O2の回転トルク）
従つて、T1＋Z1／Z2T2＝constであれば吐出し量
の変動がなく、無脈動条件を満足するが、特に、
T1＝const. T2＝０
であることが、歯車ポンプの流体力学的理想条件
である。T1＝constを満足するには、閉曲線であ
る接触点の軌跡の全体が丁度歯車の歯巾に沿つて
存在することで、ピツチ円半径をR1、R2、歯車
の歯巾をＬ、捩れ角をβ、i0を整数としたとき
tanβ＝i0R1／Ｌ2π／Z1＝i0R2／Ｌ2π／Z2＝i0mπ
／Ｌ……(3)
（ただし、ｍ：モジユール）
とすればよい。即ち歯形の捩れが歯巾Ｌに於てピ
ツチmπの整数倍であることが必要である。 PdQ=T 1 dθ 1 +T 2 dθ 2 ...(1) ∴dQ/dθ 1 = 1/P(T 1 +Z 1 /Z 2 T 2 ) ...(2) (However, T 1 : Gear O 1 Rotational torque, T 2 : Rotational torque of gear O 2 ) Therefore, if T 1 + Z 1 /Z 2 T 2 = const, there will be no fluctuation in the discharge amount and the no-pulsation condition is satisfied, but in particular, T 1 = const. T 2 =0 is the ideal hydrodynamic condition for the gear pump. In order to satisfy T 1 = const, the entire locus of the contact point, which is a closed curve, must lie exactly along the tooth width of the gear, so that the radius of the pitch circle is R 1 , R 2 , and the tooth width of the gear is L, When the torsion angle is β and i 0 is an integer, tanβ=i 0 R 1 /L2π/Z 1 =i 0 R 2 /L2π/Z 2 =i 0 mπ
/L...(3) (However, m: module) may be used. That is, it is necessary that the torsion of the tooth profile is an integral multiple of the pitch mπ in the tooth width L.
次にT2＝０となるための条件を具体的な例を
あげて説明する。 Next, the conditions for T 2 =0 will be explained using a specific example.
連続接触歯形の極限は夫々の外形線及びピツチ
円径を接触線の軌跡とする歯形で、第１図に示す
通りで図中、Ａは接触線の軌跡を示している。こ
れは歯形の実質側の関係より「接触線の軌跡の法
線は中心線分内を通らねばならない」ことから容
易に判明することである。第１図より、
cosθa1＝（１＋Z1／Z2）2＋（Z1／Z2）2−（R02／R2）
2／２Z1／Z2（１＋Z1／Z2）……(4)
cosθb1＝（１＋Z2／Z1）2＋（Z2／Z1）2＋（R01／R1）
2／２R01／R1（１＋Z2／Z1）……(5)
cosθa2＝（１＋Z2／Z1）2＋（Z2／Z1）2−（R01／R1）
2／２Z2／Z1（１＋Z2／Z1）……(6)
cosθb2＝（１＋Z1／Z2）2＋（Z1／Z2）2＋（R02／R2）
2／２R02／R2（１＋Z1／Z2）……(7)
である。但し、R01は駆動歯車の歯先円半径、
R02は従動歯車の歯先円半径である。ピツチ円上
の歯厚の含み角を1、2としたとき
1／２＝π／2Z1（１＋ε） ……(8)
2／２＝π／2Z2（１−ε） ……(9)
とするεを定めれば、歯先の含み角1、2、θa1
を駆動歯車のピツチ円上の接触点移動角度、θb1
を駆動歯車の外径上の接触点移動角度、θa2を従
動歯車のピツチ円上の接触点移動角度、θb2を従
動歯車の外径上の接触点移動角度として次式にで
与えられる。 The limit of a continuous contact tooth profile is a tooth profile whose contact line locus is the respective outline and pitch circle diameter, as shown in FIG. 1, where A indicates the contact line locus. This is easily understood from the fact that ``the normal line of the locus of the contact line must pass within the center line segment'' from the relationship on the substantial side of the tooth profile. From Figure 1, cosθa 1 = (1+Z 1 /Z 2 ) 2 + (Z 1 /Z 2 ) 2 − (R 02 /R 2 )
2 /2Z 1 /Z 2 (1 + Z 1 /Z 2 )...(4) cosθb 1 = (1 + Z 2 /Z 1 ) 2 + (Z 2 /Z 1 ) 2 + (R 01 /R 1 )
2 /2R 01 /R 1 (1+Z 2 /Z 1 )……(5) cosθa 2 = (1 + Z 2 /Z 1 ) 2 + (Z 2 /Z 1 ) 2 − (R 01 /R 1 )
2 /2Z 2 /Z 1 (1 + Z 2 /Z 1 )...(6) cosθb 2 = (1 + Z 1 /Z 2 ) 2 + (Z 1 /Z 2 ) 2 + (R 02 /R 2 )
2 /2R 02 /R 2 (1+Z 1 /Z 2 )...(7). However, R 01 is the tip circle radius of the driving gear,
R 02 is the tip circle radius of the driven gear. When the included angle of the tooth thickness on the pitch circle is 1 and 2 , 1 / 2 = π / 2Z 1 (1 + ε) ... (8) 2 / 2 = π / 2Z 2 (1 - ε) ... (9) If ε is determined, the included angle of the tooth tip 1 , 2 , θa 1
is the moving angle of the contact point on the pitch circle of the driving gear, θb 1
is the moving angle of the contact point on the outer diameter of the driving gear, θa 2 is the moving angle of the contact point on the pitch circle of the driven gear, and θb 2 is the moving angle of the contact point on the outer diameter of the driven gear, which is given by the following equation.
01／２＝π／2Z1（１＋ε）−Z2／Z1θa2＋θb1…
…(10)
01／２＝π／2Z2（１−ε）−Z1／Z2θa1＋θb2…
…(11)
また、歯形曲線のアデンダム部分の動径をρa1、
ρa2、デデンダム部分をρd1、ρd2とすると次式の
通りである。 01 /2=π/2Z 1 (1+ε)−Z 2 /Z 1 θa 2 +θb 1 …
…(10) 01 /2=π/2Z 2 (1−ε)−Z 1 /Z 2 θa 1 +θb 2 …
…(11) Also, the radius vector of the addendum part of the tooth profile curve is ρa 1 ,
When ρa 2 and the dedendum parts are ρd 1 and ρd 2 , the following equation is obtained.
（ρa1／R1）2＝１＋２Z2／Z1（１＋Z2／Z1）（１−cos
θ2） ０θ2θa2……(12)
（ρd1／R1）2＝（Rr1／R1）2＋２Z2／Z1R02／R2（１＋
Z2／Z1）（１−cosθ2） ０θ2θb2……(13)
（ρa2／R2）2＝１＋２Z1／Z2（１＋Z1／（１−cosθ1
） ０θ1θa1……(14)
（ρd2／R2）2＝（Rr2／R2）2＋２Z1／Z2R01／R1（１＋
Z1／Z2）（１−cosθ2） ０θ1θb1……(15)
次に、第２図は歯筋方向の接触線（シール線に
なる）の展開図を示すがこれによつて理論回転ト
ルクT1、T2を求めると
T1＝Ｐ／２ R1／tanβi0〔2〓a1
∫0
（R2 0−R2 1）dθ1＋２02/2
∫0
（R2 1−R2 r1）Z2／Z1dθ2
＋2〓a2
∫0 0
（R2 01−ρ2 a1）Z2／Z1dθ2−2〓b2
∫0
（R2 01−ρ2 d1）Z2／Z1dθ2〕
＝Ｐ／２R2 1Ｌ｛（R01／R1）2−１｝＋Ｐ／2πZ1R2 1Ｌ
〔｛（R01／R1）2−１｝（θb1−01／２）
−｛１−（Rr1／R1）2｝Z2／Z1（θb2−02／２）
−２（Z2／Z1）2（１＋Z2／Z1）｛θa2−sinθa2−R0
2／R1（θb2−sinθb2）｝〕……(16)
T2＝Ｐ／２ R2／tanβi0〔2〓a2
∫0
（R2 02−R2 2）dθ2＋２02/2
∫0
（R2 02−R2 r2）Z1／Z2dθ1
＋2〓a1
∫0
（R2 20−ρ2 a2）Z1／Z2dθ1−2〓b1
∫0
（R2 02−ρ2 d2）Z1／Z2dθ1〕
＝Ｐ／２R2 2Ｌ｛（R02／R2）2−１｝＋Ｐ／2πZ2R2 2Ｌ
〔｛（R02／R2）2−１｝（θb2−02／２）
−｛１−（Rr2／R2）2｝Z1／Z2（θb1−01／２）
−２（Z1／Z2）2（１＋Z1／Z2）｛θa1−sinθa1−R0
1／R1（θb1−sinθb1）｝〕……(17)
となる。ここで、T2＝０とおき、上式を整理す
ると次式の如くなる。(ρa 1 /R 1 ) 2 = 1 + 2Z 2 /Z 1 (1 + Z 2 /Z 1 ) (1-cos
θ 2 ) 0θ 2 θa 2 ...(12) (ρd 1 /R 1 ) 2 = (Rr 1 /R 1 ) 2 +2Z 2 /Z 1 R 02 /R 2 (1+
Z 2 /Z 1 ) (1-cosθ 2 ) 0θ 2 θb 2 ...(13) (ρa 2 /R 2 ) 2 = 1+2Z 1 /Z 2 (1+Z 1 /(1-cosθ 1
) 0θ 1 θa 1 ...(14) (ρd 2 /R 2 ) 2 = (Rr 2 /R 2 ) 2 +2Z 1 /Z 2 R 01 /R 1 (1+
Z 1 /Z 2 ) (1-cosθ 2 ) 0θ 1 θb 1 ...(15) Next, Figure 2 shows a developed view of the contact line (which becomes the seal line) in the direction of the tooth trace. To find the theoretical rotational torques T 1 and T 2 , T 1 = P/2 R 1 /tanβi 0 [2〓 a1 ∫ 0 (R 2 0 − R 2 1 ) dθ 1 +2 02/2 ∫ 0 (R 2 1 − R 2 r1 ) Z 2 /Z 1 dθ 2 +2〓 a2 ∫ 0 0 (R 2 01 −ρ 2 a1 )Z 2 /Z 1 dθ 2 −2〓 b2 ∫ 0 (R 2 01 −ρ 2 d1 )Z 2 /Z 1 dθ 2 ] = P/2R 2 1 L {(R 01 /R 1 ) 2 −1} + P/2πZ 1 R 2 1 L
[{(R 01 /R 1 ) 2 −1}(θb 1 − 01 /2) −{1−(Rr 1 /R 1 ) 2 }Z 2 /Z 1 (θb 2 − 02 /2) −2( Z 2 /Z 1 ) 2 (1 + Z 2 /Z 1 ) {θa 2 −sinθa 2 −R 0
2 /R 1 (θb 2 − sinθb 2 )}]……(16) T 2 = P/2 R 2 /tanβi 0 [2〓 a2 ∫ 0 (R 2 02 − R 2 2 ) dθ 2 +2 02/2 ∫ 0 (R 2 02 −R 2 r2 )Z 1 /Z 2 dθ 1 +2〓 a1 ∫ 0 (R 2 20 −ρ 2 a2 )Z 1 /Z 2 dθ 1 −2〓 b1 ∫ 0 (R 2 02 − ρ 2 d2 ) Z 1 /Z 2 dθ 1 ] = P/2R 2 2 L {(R 02 /R 2 ) 2 −1} + P/2πZ 2 R 2 2 L
[{(R 02 /R 2 ) 2 −1} (θb 2 − 02 /2) −{1−(Rr 2 /R 2 ) 2 }Z 1 /Z 2 (θb 1 − 01 /2) −2( Z 1 /Z 2 ) 2 (1 + Z 1 /Z 2 ) {θa 1 −sinθa 1 −R 0
1 /R 1 (θb 1 − sinθb 1 )}]...(17) Here, by setting T 2 =0 and rearranging the above equation, the following equation is obtained.
ε＝〔１−｛１−Z1／Z2（R01／R1−１）｝2〕Z2／Z1θ
a2−｛（R02／R2）2−１｝θa1／π／2Z1〔（R02／R2）
2−｛１−Z1／Z2（R02／R1−１）｝2
＋２Z1／Z2（１＋Z1／Z2）｛θa1−sinθa1−R01／R1
（θb1−sinθb1｝／π／2Z1〔（R02／R2）2−｛１−Z1
／Z2（R02／R1−１）｝2−１……(18)
特に、R02／R2＝１即ち駆動車は全アデンダム
歯車、従動車は全デデンダム歯車とすると
ε＝2Z2／πθa2−4Z1／πZ1／Z2（１＋Z1／Z2）R01／R
1（θb1−sinθb1）／１−｛１−Z1／Z2（R01／R1−１
）｝2−１……(19)
となる。ε=[1-{1-Z 1 /Z 2 (R 01 /R 1 -1)} 2 ]Z 2 /Z 1 θ
a 2 − {(R 02 /R 2 ) 2 −1}θa 1 /π/2Z 1 [(R 02 /R 2 )
2 −{1−Z 1 /Z 2 (R 02 /R 1 −1)} 2 +2Z 1 /Z 2 (1+Z 1 /Z 2 ) {θa 1 −sinθa 1 −R 01 /R 1
(θb 1 −sinθb 1 }/π/2Z 1 [(R 02 /R 2 ) 2 −{1−Z 1
/Z 2 (R 02 /R 1 -1)} 2 -1...(18) In particular, if R 02 /R 2 = 1, that is, the driving wheel is all addendum gears and the driven wheel is all addendum gears, ε=2Z 2 /πθa 2 −4Z 1 /πZ 1 /Z 2 (1+Z 1 /Z 2 )R 01 /R
1 (θb 1 −sinθb 1 )/1−{1−Z 1 /Z 2 (R 01 /R 1 −1
)} 2 −1……(19).
第３図は、Z1＝６、Z2＝３、４、５、６、７と
したときの各場合について求めたもので、◎印は
従動車の歯厚限界を示す。 Figure 3 shows the results obtained for each case when Z 1 = 6 and Z 2 = 3, 4, 5, 6, and 7, and the mark ◎ indicates the tooth thickness limit of the driven wheel.
第４図はZ1＝６、Z2＝４ R01／R1＝1.3 R02／
R2＝１としたときの夫々の歯形の実際図を示し、
この例では、ａ〜ｅの５個の連続接触点を有して
おり、T2＝０なるためにはε＝0.5758である。 In Figure 4, Z 1 = 6, Z 2 = 4 R 01 /R 1 = 1.3 R 02 /
The actual diagram of each tooth profile when R 2 = 1 is shown,
In this example, there are five consecutive contact points a to e, and for T 2 =0, ε=0.5758.
次に、連続接触点が常に１個所の場合について
説明するが、この場合においても、前記(1)〜(3)式
はそのまま当てはまる。次に、T2＝０なるため
の条件について説明すると、この場合、第５図に
於て、接触点の軌跡が従動車の外形R02とピツチ
点Ｐを中心とした円とする一点連続接触歯形で
R02／R2１の場合にのみT2＝０であり、これ以
外にない。第５図より、
cosθa2＝１＋（R02／R2）2−（Z1／Z2）−12（R01／R1
）2／２R02／R2
……（20）
2／２＝π／2Z1（１−ε）……（21）
01／２＝π／2Z1（１＋ε）−Z2／Z1θa2……（2
2）
（ρa1／R1）2＝（Rr1／R1）2＋２Z2／Z1R02／R2（１−
cosθ2）
……（23）
である。 Next, a case where there is always one continuous contact point will be explained, but even in this case, the above equations (1) to (3) apply as they are. Next, we will explain the conditions for T 2 = 0. In this case, in Fig. 5, there is a one-point continuous contact where the locus of the contact point is a circle centered on the outer shape R 02 of the driven vehicle and the pitch point P. in tooth shape
T 2 =0 only if R 02 /R 2 1, and no other case. From Figure 5, cosθa 2 = 1 + (R 02 /R 2 ) 2 − (Z 1 /Z 2 )−1 2 (R 01 /R 1
) 2 /2R 02 /R 2
...(20) 2 /2=π/2Z 1 (1-ε) ...(21) 01 /2=π/2Z 1 (1+ε)-Z 2 /Z 1 θa 2 ...(2
2) (ρa 1 /R 1 ) 2 = (Rr 1 /R 1 ) 2 +2Z 2 /Z 1 R 02 /R 2 (1-
cosθ 2 ) ...(23).
次に、第６図は歯筋方向の接触線（シール線に
なる）の展開図を示すがこれによつて理論回転ト
ルクT1、T2を求めると
T1＝Ｐ／２R1／tanβi0〔２02/2
∫0
（R2 r1−R2r1）Z2／Z1dθ2＋26 a22
∫0
（R2 01−ρ2 a1）Z2／Z1dθ2〕
Ｐ／２R2 1Ｌ｛（R01／R1）2−（Rr1／R1）2｝−Ｐ／2
πZ1R2 1Ｌ〔｛R01／R1）2−（Rr1／R1）2｝01／２
＋２（Z2／Z1）2（１＋Z2／Z1）R02／R2（θa2−sin
θa2）〕……（24）
T2＝Ｐ／２ R2／tanβi0〔２01/2
∫
∫0
（R2 02−R2 r2）Z1／Z2dθ1〕＝Ｐ／4πZ1 01R2 2Ｌ｛
（R02／R2）2−（Rr2／R2）｝……（25）
となる。従つて01＝０であればT2＝０となる。
故に
ε＝2Z2／πcos-1１＋（R02／R2）2−（Z1／Z2）2（R01
／R1−１）2／２R02／R2−１……（26）
となり、特にR02／R2＝１であれば
ε＝2Z2／πcos-1｛１−１／２（Z1／Z2）2（R01／R1−
１）2｝−１
……（27）
となる。 Next, Fig. 6 shows a developed view of the contact line (which becomes the seal line) in the direction of the tooth trace, and from this, the theoretical rotational torques T 1 and T 2 are determined as T 1 =P/2R 1 /tanβi 0 [2 02/2 ∫ 0 (R 2 r1 −R 2 r 1 )Z 2 /Z 1 dθ 2 +2 6 a22 ∫ 0 (R 2 01 −ρ 2 a1 )Z 2 /Z 1 dθ 2 ] P/2R 2 1 L {(R 01 /R 1 ) 2 −(Rr 1 /R 1 ) 2 }−P/2
πZ 1 R 2 1 L [{R 01 /R 1 ) 2 − (Rr 1 /R 1 ) 2 } 01 /2 +2(Z 2 /Z 1 ) 2 (1+Z 2 /Z 1 )R 02 /R 2 ( θa 2 −sin
θa 2 )]...(24) T 2 =P/2 R 2 /tanβi 0 [2 01/2 ∫ ∫ 0 (R 2 02 −R 2 r2 )Z 1 /Z 2 dθ 1 ] = P/4πZ 1 01 R 2 2 L {
(R 02 /R 2 ) 2 − (Rr 2 /R 2 )}...(25). Therefore, if 01 = 0, T 2 = 0.
Therefore, ε=2Z 2 /πcos -1 1+(R 02 /R 2 ) 2 −(Z 1 /Z 2 ) 2 (R 01
/R 1 -1) 2 /2R 02 /R 2 -1...(26) In particular, if R 02 /R 2 = 1, ε=2Z 2 /πcos -1 {1-1/2(Z 1 /Z 2 ) 2 (R 01 /R 1 −
1) 2 }-1 ...(27) becomes.
第７図にZ1＝６、Z2＝３、４、５、６、７とし
たとの場合について求めたもので図中◎印は従動
車の歯厚限界を示す。 Figure 7 shows the results obtained for the cases where Z 1 = 6 and Z 2 = 3, 4, 5, 6, and 7, and the ◎ mark in the figure indicates the tooth thickness limit of the driven wheel.
第８図はZ1＝６、Z2＝４ R01／R1＝1.4 R02／
R2＝１としたときの夫々の歯形の実際図を示し、
T2＝０なるためにはε＝0.5518である。 In Figure 8, Z 1 = 6, Z 2 = 4 R 01 /R 1 = 1.4 R 02 /
The actual diagram of each tooth profile when R 2 = 1 is shown,
For T 2 =0, ε=0.5518.
以上の説明から明らかなように、本発明による
と、歯形の接触部分に全く力がかからないので、
歯形の摩耗、損傷等が全く生じない連続接触歯車
ポンプを提供することができる。 As is clear from the above explanation, according to the present invention, no force is applied to the contact portion of the tooth profile.
It is possible to provide a continuous contact gear pump in which tooth profile wear and damage do not occur at all.
第１図乃至第４図は、本発明の一実施例を説明
するための図、第５図乃至第８図は、本発明の他
の実施例を説明するための図で、第１図及び第５
図は基本歯形図、第２図及び第６図は、歯筋方向
の接触線の展開図、第３図及び第７図は、従動車
の歯圧限界を示す図、第４図及び第８図は、歯形
の実際図を示す図である。
O1……駆動歯車、O2……従動歯車。
1 to 4 are diagrams for explaining one embodiment of the present invention, and FIGS. 5 to 8 are diagrams for explaining other embodiments of the present invention. Fifth
The figure is a basic tooth profile diagram, Figures 2 and 6 are development diagrams of the contact line in the direction of the tooth trace, Figures 3 and 7 are diagrams showing the tooth pressure limit of the driven wheel, and Figures 4 and 8. The figure is a diagram showing an actual view of the tooth profile. O 1 ...driving gear, O 2 ...driven gear.
Claims (1)
駆動歯車と従動歯車とからなる連続接触歯形を回
転子とする歯車ポンプにおいて、前記駆動歯車の
歯数をZ1、ピツチ円半径をR1、歯先円半径を
R01、ピツチ円上の歯厚の含み角を1、ピツチ円
上の接触点移動角度をθa1、外径上の接触点移動
角度をθb1とし、前記従動歯車の歯数をZ2、ピツ
チ円半径をR2、歯先円半径をR02、ピツチ円上の
歯厚の含み角を2、ピツチ円上の接触点移動角
度をθa2、外径上の接触点移動角度をθb2としたと
きtanβ＝i0mπ／Ｌ（i0…整数）の条件で、 1＝π／Z1（１＋ε）および2＝π／Z2（１−ε） を定め、εの値を ε＝〔１−｛１−Z1／Z2（R01／R1−１）｝2〕Z2
／Z1θa2−｛（R02／R2）2−１｝θa1／π／2Z1〔（R02
／R2）2−｛１−Z1／Z2（R02／R1−１｝2 ＋２Z1／Z2（１＋Z1／Z2）｛θa1−sinθa1−R
01／R1（θb1−sinθb1｝／π／2Z1〔（R02／R2）2−｛
１−Z1／Z2（R02／R1）−１）｝2−１ から、流体の吐出し圧力による駆動歯車の理論ト
ルクが常に略一定であり、且つ従動歯車の理論ト
ルクが略零となるごとく定めたことを特徴とする
連続接触歯車ポンプ。 ２ 前記連続接触点が１箇所乃至複数箇所である
ことを特徴とする特許請求の範囲第１項記載の連
続接触歯車ポンプ。 ３ 前記連続接触点が常に１箇所であることを特
徴とする特許請求の範囲第１項記載の連続接触歯
車ポンプ。[Scope of Claims] 1. A gear pump whose rotor is a continuous contact tooth profile consisting of a driving gear and a driven gear of module m, both of which have a face width L and a helix angle β, and the number of teeth of the driving gear is Z 1 and the pitch is The circle radius is R 1 and the tooth tip circle radius is
R 01 , the included angle of the tooth thickness on the pitch circle is 1 , the contact point movement angle on the pitch circle is θa 1 , the contact point movement angle on the outer diameter is θb 1 , the number of teeth of the driven gear is Z 2 , The pitch circle radius is R 2 , the tip circle radius is R 02 , the included angle of the tooth thickness on the pitch circle is 2 , the contact point movement angle on the pitch circle is θa 2 , the contact point movement angle on the outer diameter is θb 2 Then, under the condition of tanβ=i 0 mπ/L (i 0 ...integer), 1 = π/Z 1 (1+ε) and 2 = π/Z 2 (1−ε) are determined, and the value of ε is set as ε= [1-{1-Z 1 /Z 2 (R 01 /R 1 -1)} 2 ]Z 2
/Z 1 θa 2 −{(R 02 /R 2 ) 2 −1}θa 1 /π/2Z 1 [(R 02
/R 2 ) 2 −{1−Z 1 /Z 2 (R 02 /R 1 −1} 2 +2Z 1 /Z 2 (1+Z 1 /Z 2 ) {θa 1 −sinθa 1 −R
01 /R 1 (θb 1 −sinθb 1 }/π/2Z 1 [(R 02 /R 2 ) 2 −{
1-Z 1 /Z 2 (R 02 /R 1 )-1)} 2-1 , the theoretical torque of the driving gear due to the fluid discharge pressure is always approximately constant, and the theoretical torque of the driven gear is approximately zero. A continuous contact gear pump characterized by the following: 2. The continuous contact gear pump according to claim 1, wherein the number of continuous contact points is one or more. 3. The continuous contact gear pump according to claim 1, wherein the continuous contact point is always one.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP8114983A JPS59206689A (en) | 1983-05-10 | 1983-05-10 | Continuous contact gear pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP8114983A JPS59206689A (en) | 1983-05-10 | 1983-05-10 | Continuous contact gear pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS59206689A JPS59206689A (en) | 1984-11-22 |
| JPH0510514B2 true JPH0510514B2 (en) | 1993-02-09 |
Family
ID=13738370
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP8114983A Granted JPS59206689A (en) | 1983-05-10 | 1983-05-10 | Continuous contact gear pump |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS59206689A (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111520454B (en) * | 2020-04-26 | 2022-05-06 | 宿迁学院 | Design method of lightweight gear pair for aerospace low-pulsation micropump |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5029161A (en) * | 1973-07-17 | 1975-03-25 | ||
| JPS5389763A (en) * | 1977-01-19 | 1978-08-07 | Oval Eng Co Ltd | Volumetric flow meter |
| JPS5424057A (en) * | 1977-07-25 | 1979-02-23 | Oval Eng Co Ltd | Rotor of positive displacement flowmeter |
-
1983
- 1983-05-10 JP JP8114983A patent/JPS59206689A/en active Granted
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5029161A (en) * | 1973-07-17 | 1975-03-25 | ||
| JPS5389763A (en) * | 1977-01-19 | 1978-08-07 | Oval Eng Co Ltd | Volumetric flow meter |
| JPS5424057A (en) * | 1977-07-25 | 1979-02-23 | Oval Eng Co Ltd | Rotor of positive displacement flowmeter |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS59206689A (en) | 1984-11-22 |
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