KR101237112B1 - Gear pump - Google Patents

Gear pump Download PDF

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Publication number
KR101237112B1
KR101237112B1 KR1020087001995A KR20087001995A KR101237112B1 KR 101237112 B1 KR101237112 B1 KR 101237112B1 KR 1020087001995 A KR1020087001995 A KR 1020087001995A KR 20087001995 A KR20087001995 A KR 20087001995A KR 101237112 B1 KR101237112 B1 KR 101237112B1
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South Korea
Prior art keywords
tooth
teeth
gears
gear
thickness
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KR1020087001995A
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Korean (ko)
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KR20080025179A (en
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기이치 고가네이
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카야바 고교 가부시기가이샤
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C2/14—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C2/18—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with similar tooth forms
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/082—Details specially related to intermeshing engagement type machines or pumps
    • F04C2/084—Toothed wheels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps

Abstract

한쌍의 기어의 톱니가 서로 맞물릴 때, 톱니의 각(角)에 형성된 응착(凝着)된 톱니끝이 대향하는 톱니의 톱니면을 깍거나, 서로 맞물리는 톱니면과의 사이에서 변형하는 일이 없는 기어펌프이다. 서로 맞물리는 톱니면(3,4)을 인볼류트곡선(involute curve)을 따라서 형성하는 동시에, 그 톱니(1a,2a)의 선단에 설계상의 톱니끝의 두께(t0)를 확보한 한쌍의 기어(1,2)를 제로 백래쉬(zero backlash)를 유지하여 서로 맞물려서 이루어지는 기어펌프에 있어서, 상기 기어(1,2)의 톱니(1a,2a)는 그 회전방향의 후방에 위치하는 톱니면(3,4)과 톱니끝면(10,11)에서 형성되는 각(P1,P2)을 커트한 후의 톱니끝의 두께(t1)를 설계상의 톱니끝의 두께(t0)보다도 얇게 하였다.When teeth of a pair of gears engage with each other, the toothed surfaces of the teeth formed on the teeth of the tooth teeth are shaved or deformed between the teeth face that meshes with each other. Without gear pump. A pair of gears in which the tooth surfaces 3 and 4 meshing with each other are formed along an involute curve, and the thickness t 0 of the design tooth tip is secured at the tip of the tooth 1a and 2a. In a gear pump in which (1, 2) is held in engagement with each other while maintaining a zero backlash, the teeth 1a, 2a of the gears 1, 2 are tooth surfaces 3 located rearward in the rotational direction thereof. And 4) and the thickness t 1 of the tooth tip after cutting the angles P1 and P2 formed on the tooth tip surfaces 10 and 11 were made thinner than the thickness t 0 of the design tooth tip.

Description

기어펌프{GEAR PUMP}Gear Pump {GEAR PUMP}

본 발명은 토출맥동(脈動)의 진폭을 억제하기 위하여 백래쉬(backlash)를 매우 작게 한 제로백래시(Zero backlash)의 기어펌프에 관한 것이다.BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a zero backlash gear pump having a very small backlash in order to suppress the amplitude of discharge pulsation.

유압제어장치의 소음은, 주로 유압펌프의 토출맥동의 진폭에 원인이 있다고 일반적으로 생각되고 있다. 그리고 기어펌프에 있어서는 이 토출맥동의 진폭을 작게하기 위하여 기어의 맞물림부분의 극간인 이른바, 백래시(backlash)를 무한하게 제로에 가깝게 한 펌프가 알려져 있다. 이러한 종류의 기어펌프는, 일반적으로 제로백래시(Zero backlash) 기어펌프라 불리고 있다.It is generally considered that the noise of the hydraulic control device is mainly caused by the amplitude of the discharge pulsation of the hydraulic pump. In the gear pump, in order to reduce the amplitude of this discharge pulsation, there is known a pump in which the backlash is infinitely close to zero, which is the gap between the engagement portions of the gears. This type of gear pump is generally called a zero backlash gear pump.

도 3 및 도 4에 종래의 제로백래시 기어펌프를 도시한다. 도 3에 도시하는 바와 같이, 종래의 제로백래시 기어펌프는, 기어케이스(G)의 동체내경(body bore)(b1,b2)에 한쌍의 기어(1,2)를 내장하고 있다. 이 기어(1,2)는 도 4에 도시하는 바와 같이 그 톱니(1a,2a)의 톱니면(3,4)을 인볼류트곡선을 따라서 형성하고 있다. 또 상기 톱니(1a,2a)의 톱니끝의 두께(t0)는, 톱니수, 공구압력각 및 톱니끝면의 직경 등, 기어의 설계제원을 따라서 필연적으로 결정되는 것이다. 3 and 4 show a conventional zero backlash gear pump. As shown in FIG. 3, the conventional zero backlash gear pump incorporates a pair of gears 1 and 2 in the body bore b1 and b2 of the gear case G. As shown in FIG. As shown in Fig. 4, the gears 1 and 2 form tooth surfaces 3 and 4 of the teeth 1a and 2a along the involute curve. In addition to that the teeth (1a, 2a) thickness (t 0) of the teeth of the end, the number of teeth, such as the diameter of the tool pressure and the end face of each tooth, thus inevitably determined by the design specification of the gear.

상기와 같이 한 제로백래시 기어펌프는 연습운전시에 기어(1,2)가 기어케이스(G)의 토출실(5) 측으로부터 흡입실(6)측으로 내리누름으로써, 기어(1,2)의 톱니(1a,2a)가 흡입실(6)에 인접하는 동체내경(b1,b2)의 내면을 얇게 깍아서, 즉 기어트랙(7,7)을 형성한다(도 3 참조). In the zero backlash gear pump as described above, the gears 1 and 2 are pushed down from the discharge chamber 5 side of the gear case G to the suction chamber 6 side during the practice operation. The teeth 1a, 2a are thinly cut into the inner surfaces of the fuselage inner diameters b1, b2 adjacent to the suction chamber 6, that is, the gear tracks 7, 7 are formed (see FIG. 3).

상기와 같이 동체내경(b1,b2)에 기어트랙(7,7)을 형성함으로써 기어(1,2)의 톱니(1a,2a)와 동체내경(b1,b2)의 내면과의 톱니끝의 극간이 최소로 유지된다. 이에 따라서 톱니끝으로부터의 내부 누설을 최소로 하는 것이 가능하고, 상기 펌프는 작동오일을 효율적으로 토출하는 것이 가능하다.As described above, the gear tracks 7 and 7 are formed in the fuselage inner diameters b1 and b2 so that the gap between the teeth 1a and 2a of the gears 1 and 2 and the inner surface of the fuselage inner diameters b1 and b2 is inclined. This is kept to a minimum. Accordingly, it is possible to minimize the internal leakage from the tooth tip, and the pump can discharge the operating oil efficiently.

단, 상기와 같이 기어트랙(7,7)을 형성하는 과정에서 기어(1,2)의 톱니(1a,2a)에는 그 회전방향(R)의 후방에 위치하는 톱니면(3,4)과 톱니끝면(10,11)에서 형성되는 각(角)(P1,P2)에 기어케이스(G)의 금속이 응착(凝着)되고, 도 4에 도시하는 응착된 톱니끝(8,9)이 형성되어 버린다.However, in the process of forming the gear tracks 7 and 7 as described above, the teeth 1a and 2a of the gears 1 and 2 are provided with tooth surfaces 3 and 4 located behind the rotational direction R thereof. The metal of the gear case G is adhered to the angles P1 and P2 formed at the tooth end surfaces 10 and 11, and the bonded tooth tips 8 and 9 shown in FIG. It is formed.

특허문헌 1: 일본국 특개 2001-289180호 공보Patent Document 1: Japanese Patent Application Laid-Open No. 2001-289180

상기 제로백래시(zero backlash) 기어펌프에서는, 상술한 바와 같이 기어(1,2)의 톱니(1a,2a)가 기어트랙(7,7)을 형성하는 과정으로, 톱니(1a,2a)의 각(角)(P1,P2)에 응착된 톱니끝(8,9)이 형성되어 버린다. In the zero backlash gear pump, as described above, the teeth 1a and 2a of the gears 1 and 2 form the gear tracks 7 and 7, and thus the angles of the teeth 1a and 2a. (I) The tooth tips 8 and 9 adhered to P1 and P2 are formed.

톱니(1a,2a)의 각(角)(P1,P2)에 응착된 톱니끝(8,9)이 형성되면, 도 5에 도시하는 바와 같이 기어(1)의 톱니(1a)와 기어(2)의 톱니(2a)가 서로 맞물릴 때, 상기 응착된 톱니끝(8)은 대향하는 기어(2)의 톱니(2a)의 톱니면(4)에 강하게 눌려서 변형된다. 마찬가지로, 상기 응착된 톱니끝(9)도 대향하는 톱니(1a)의 톱니면(3)에 강하게 눌려서 변형된다. 이때 톱니면(3,4)에는 조흔(條痕)이 형성되고, 이 조흔(條痕)은 톱니면(3,4)의 톱니면 조도(粗度)나 기어정밀도를 악화시킨다. 그 때문에 이 조흔이 형성됨으로써 소음이 발생한다는 문제가 있었다.When the tooth tips 8 and 9 bonded to the angles P1 and P2 of the teeth 1a and 2a are formed, the teeth 1a and the gear 2 of the gear 1 are shown in FIG. When the teeth 2a of the mesh member engage with each other, the bonded tooth tip 8 is deformed by being strongly pressed against the tooth surface 4 of the tooth 2a of the opposing gear 2. Similarly, the bonded tooth tip 9 is also deformed by being strongly pressed against the tooth surface 3 of the opposing tooth 1a. At this time, streaks are formed on the tooth surfaces 3 and 4, and the streaks deteriorate the roughness of the teeth of the tooth surfaces 3 and 4 and the gear precision. Therefore, there was a problem that noise was generated by the formation of this streak.

또 상기 제로백래시 기어펌프는 그 백래시가 매우 작기 때문에, 한쌍의 기어(1,2)의 사이에는 거의 유격(裕隔)이 없다. 이 때문에 응착된 톱니끝(8,9)이 톱니면(3,4) 사이에서 변형될 때에 기어(1,2)에는 기어트랙(7,7) 방향으로 이동하는 힘이 작용한다.In addition, since the backlash of the zero backlash gear pump is very small, there is almost no play between the pair of gears 1 and 2. For this reason, the force moving in the direction of the gear tracks 7 and 7 acts on the gears 1 and 2 when the bonded tooth tips 8 and 9 are deformed between the tooth surfaces 3 and 4.

상기와 같이 기어(1,2)에 기어트랙(7,7) 방향의 힘이 작용하면, 기어(1,2)의 회전중심이 겨우 이동하고, 톱니(1a,2a)가 그 이동분 만큼 새롭게 기어케이스(G)를 깍아서 그 기어트랙(7,7)을 더 깊게 해버린다. 이에 따라서 기어(1,2)와 기어트랙(7,7)과의 사이에 극간이 생겨버린다.When the force in the gear tracks 7 and 7 acts on the gears 1 and 2 as described above, the center of rotation of the gears 1 and 2 is barely moved, and the teeth 1a and 2a are newly updated by the movements. Sharpen the gear case (G) to deepen the gear tracks (7, 7). As a result, a gap is generated between the gears 1 and 2 and the gear tracks 7 and 7.

상기와 같이 기어(1,2)와 기어트랙(7,7)과의 사이에 극간이 생기면, 그 극간으로부터 내부누설이 발생하고, 펌프의 토출량이 저하되어 버린다. 또 제로 백래시로 함으로써 토출 맥동진폭을 억제는 하지만, 상기 극간으로부터의 누설에 의해 반대로 토출맥동진폭을 크게 하여 소음을 악화시켜 버린다는 문제가 있었다. If a gap is generated between the gears 1 and 2 and the gear tracks 7, 7 as described above, internal leakage occurs from the gap, and the discharge amount of the pump is reduced. In addition, although the discharge pulsation amplitude is suppressed by setting it to zero backlash, there is a problem that the discharge pulsation amplitude is increased by increasing leakage pulsation amplitude due to leakage from the gap.

본 발명의 목적은 한쌍의 기어 톱니가 서로 맞물릴 때, 톱니의 각에 형성된 응착된 톱니끝이 대향하는 톱니면에 강하게 눌려서 변형되는 일이 없는 기어펌프를 제공하는 것이다.It is an object of the present invention to provide a gear pump which, when a pair of gear teeth are engaged with each other, is not deformed by being strongly pressed against the opposing tooth surfaces formed at the angle of the teeth.

본 발명은, 서로 인접하는 면인 톱니면을 인볼류트곡선(involute curve)을 따라서 형성하는 동시에, 그 톱니의 선단에 설계상의 톱니끝의 두께(t0)를 확보한 한쌍의 기어를, 제로 백래시를 유지하여 맞물려서 이루어지는 기어펌프에 있어서, 상기 기어의 톱니는 그 회전방향의 후방에 위치하는 톱니면과 톱니끝면에서 형성되는 각을 커트한 후의 톱니끝의 두께(t1)를 설계상의 톱니끝의 두께(t0)보다도 얇게한 것을 특징으로 한다.The present invention provides a pair of gears that form tooth surfaces, which are surfaces adjacent to each other, along an involute curve, and secure the thickness t 0 of the design tooth tip at the tip of the tooth, and zero backlash. In the gear pump which is held and engaged, the tooth of the gear is the thickness of the tooth tip after designing the thickness t 1 of the tooth tip after cutting the angle formed at the tooth face and the tooth tip face located in the rear of the rotational direction. It is characterized by being thinner than (t 0 ).

본 발명에 따르면, 기어의 톱니 중, 그 회전방향의 후방에 위치하는 단면과 톱니끝면에서 형성되는 각을 커트한 후의 톱니끝의 두께(t1)를 설계상의 톱니끝의 두께(t0)보다도 얇게 하였으므로, 한쌍의 기어의 톱니가 서로 맞물리는 때, 상기 톱니의 각에 형성된 응착된 톱니끝이 대향하는 톱니면을 강하게 눌려서 변형되는 일이 없다. 따라서, 펌프의 토출량저하나 토출맥동진폭의 증가에 따른 소음을 억제하는 것이 가능하다.According to the present invention, among the teeth of the gear, the thickness t1 of the tooth tip after cutting the angle formed at the end face and the tooth tip face located behind the rotation direction is made thinner than the thickness t 0 of the tooth tip design. Therefore, when the teeth of a pair of gears are engaged with each other, the bonded toothed ends formed at the angles of the teeth do not depress strongly by depressing the opposing tooth surfaces. Therefore, it is possible to suppress the noise caused by the discharge amount of the pump or the increase in the discharge pulsation amplitude.

도 1은, 본 발명의 제1실시형태에서의 기어의 톱니를 도시한 확대도이다.1 is an enlarged view showing the teeth of a gear in the first embodiment of the present invention.

도 2는, 제2 실시형태에서의 기어의 톱니를 도시한 확대도이다.FIG. 2 is an enlarged view showing the teeth of the gear in the second embodiment. FIG.

도 3은, 기어펌프의 단면도이다.3 is a cross-sectional view of the gear pump.

도 4는, 종래의 기어의 톱니를 도시한 확대도이다.4 is an enlarged view showing the teeth of a conventional gear.

도 5는, 도 3의 부분확대도이다.5 is a partially enlarged view of FIG. 3.

※부호의 설명※※ Explanation of symbols ※

1,2…기어 1a,2a…기어의 톱니1,2... Gear 1a, 2a... Cogwheel of gear

3,4…톱니면 10,11…톱니끝면3,4... 10,11... Tooth end surface

P1,P2…톱니의 회전방향 후방의 톱니면과 톱니끝면에서 형성되는 각P1, P2... Angle formed at the tooth side and the tooth end surface of the tooth rearward

t0…설계상의 톱니끝의 두께 t1…본 발명의 톱니끝의 두께t 0 . Design thickness of tooth tip t 1 . Thickness of the tooth tip of the present invention

R…회전방향 S1,S2…커트면R… Rotation direction S1, S2... Cut cotton

T1,T2…커트면T1, T2... Cut cotton

도 1에 본 발명의 제1 실시형태를 도시하였으나, 본 발명은 기어(1,2)의 톱니(1a,2a)에 특징이 있으며, 그외의 구성은 상기 종래예와 동일하다. 따라서, 이하에서는 종래와 동일한 구성에 대해서는 동일한 부호를 부여한다.Although the 1st Embodiment of this invention was shown in FIG. 1, this invention is characterized by the teeth 1a, 2a of the gears 1 and 2, The other structure is the same as that of the said prior art example. Therefore, below, the same code | symbol is attached | subjected about the same structure as before.

도 1에 도시하는 바와 같이, 기어(1,2)의 톱니(1a,2a)는 그 회전방향(R)과 반대측의 톱니면(3,4)과, 톱니끝면(10,11)에서 형성되는 각(角)(P1,P2)을 커트하여 그 톱니끝의 두께(t1)를 설계상의 톱니끝의 두께(t0)보다도 얇게 하고 있다.As shown in Fig. 1, the teeth 1a, 2a of the gears 1, 2 are formed at the tooth surfaces 3, 4 on the side opposite to the rotational direction R thereof, and at the tooth end surfaces 10, 11; The angles P1 and P2 are cut to make the thickness t 1 of the tooth tip thinner than the thickness t 0 of the tooth tip in design.

구체적으로는, 상기 톱니(1a,2a)의 각(P1,P2)을 톱니끝의 두께방향으로 (0.07~0.35)×t0만 커트하여 커트면(S1, S2)을 형성하고 있다. 즉, 상기 톱니끝의 두께(t1)가 t0-(0.07~0.35)×t0를 이루는 관계로 되어 있다.Specifically, the cut surfaces S1 and S2 are formed by cutting the angles P1 and P2 of the teeth 1a and 2a only in the thickness direction of the tooth tip (0.07 to 0.35) x t 0 . That is, the thickness (t 1) of the tooth tip t 0 - is the relationship between the forms (0.07 ~ 0.35) × t 0 .

또 톱니길이방향의 높이(l)는 기어(1,2)의 원활한 맞물림에 지장이 없는 범 위내, 즉 (0.05~0.15)×m(m:모듈)만 커트하도록 하고 있다.In addition, the height l in the tooth length direction cuts only in the range where the gears 1 and 2 are smoothly engaged, that is, (0.05 to 0.15) x m (m: module).

상기와 같이, 톱니(1a,2a)의 각(P1,P2)을 톱니끝의 두께방향으로 (0.07×0.35)×t0만 커트한 것은 실험에서 이하의 것을 알 수 있었기 때문이다.As described above, the fact that only the angles P1 and P2 of the teeth 1a and 2a were cut (0.07 x 0.35) x t 0 in the thickness direction of the tooth tip was found in the experiment.

먼저, 상기 각(P1,P2)을 0.35×t0보다 많게 커트하면, 맞물림 톱니면 길이가 감소하고, 맞물림률이 저하된다.First, when the angles P1 and P2 are cut more than 0.35 × t 0 , the engagement tooth surface length decreases and the engagement rate decreases.

반대로, 상기 각(P1,P2)을 0.07×t0보다 적게 커트하면, 톱니(1a,2a)의 커트면(S1,S2)에 응착된 톱니끝(8,9)이 형성된 때, 그 응착된 톱니끝(8,9)이 대향하는 톱니(2a,1a)의 톱니면(3,4)에 강하게 눌려서 변형된다. 즉, 종래의 문제를 해결하는 것이 불가능하다.On the contrary, when the angles P1 and P2 are cut less than 0.07 × t 0 , when the toothed ends 8 and 9 are formed on the cut surfaces S1 and S2 of the teeth 1a and 2a, they are adhered. The tooth tips 8, 9 are strongly pressed against the tooth surfaces 3, 4 of the teeth 2a, 1a facing each other and deformed. That is, it is impossible to solve the conventional problem.

상기 실험결과로부터, 상기 톱니(1a,2a)의 각(P1,P2)을 커트하여 상기 톱니끝의 두께(t1)를 t0-(0.07~0.35)×t0를 이루는 관계로 하면, 톱니(1a),(2a)의 커트면(S1,S2)에 응착된 톱니끝(8,9)이 형성되어도 이들 응착된 톱니끝(8,9)이 대향하는 톱니면(3,4)에 강하게 눌려서 변형되는 일이 없다.When the angles P1 and P2 of the teeth 1a and 2a are cut from the experimental results, the thickness t 1 of the tooth tip is made t 0 − (0.07 to 0.35) × t 0 . Even if the tooth tips 8 and 9 bonded to the cut surfaces S1 and S2 of (1a) and (2a) are formed, these bonded tooth tips 8 and 9 are strongly opposed to the tooth surfaces 3 and 4 facing each other. It is not pressed and deformed.

이와 같이, 톱니(1a,2a)의 커트면(S1,S2)에 응착된 톱니끝(8,9)이 형성되어도, 한쌍의 기어(1,2)의 톱니(1a,2a)가 서로 맞물릴 때, 상기 응착된 톱니끝(8,9)이 대향하는 톱니면(3,4)에 강하게 눌려서 변형되는 일이 없으므로, 톱니면(3,4)의 톱니면 조도나 기어정밀도가 악화되지 않고, 소음을 억제하는 것이 가능하다.In this way, even when the tooth tips 8 and 9 bonded to the cut surfaces S1 and S2 of the teeth 1a and 2a are formed, the teeth 1a and 2a of the pair of gears 1 and 2 are engaged with each other. At this time, since the adhered tooth tips 8 and 9 are hardly pressed against the tooth surfaces 3 and 4 opposite to each other, the tooth surface roughness and gear precision of the tooth surfaces 3 and 4 are not deteriorated. It is possible to suppress the noise.

또 한쌍의 기어(1,2)와 기어트랙(7,7)이 새로 깍여서 톱니(1a,2a)와 동체내경(b1,b2)의 내면과의 톱니끝의 극간이 증가하는 일도 없다. 따라서 토출량의 저 하나 토출맥동진폭의 증가에 따른 소음을 억제하는 것이 가능하다.In addition, the pair of gears 1 and 2 and the gear tracks 7 and 7 are newly cut so that the clearance gap between the teeth 1a and 2a and the inner surface of the fuselage inner diameters b1 and b2 does not increase. Therefore, it is possible to suppress the noise accompanying the low discharge amount and the increase in the discharge pulsation amplitude.

또한, 상기 제1 실시형태에서는 기어(1,2)의 톱니(1a,2a)는 그 각(P1,P2)을 커트하여 커트면(S1,S2)을 형성하도록 하고 있지만, 도 2에 도시하는 제2실시형태와 같이 상기 각(P1,P2)과 반대측의 각을 톱니끝의 두께방향으로 (0.07~0.35)×t0만 커트하여 커트면(T1,T2)을 형성하도록 해도 된다. 이와 같이 기어(1a,2a)의 양측에 커트면(S1,S2) 및 (T1,T2)을 형성하면 기어(1,2)를 표리관계없이 기어케이스(G)에 내장하는 것이 가능하다.In the first embodiment, the teeth 1a, 2a of the gears 1, 2 cut the angles P1, P2 so as to form the cut surfaces S1, S2. As in the second embodiment, the angles opposite to the angles P1 and P2 may be cut only in the thickness direction of the tooth tip (0.07 to 0.35) x t 0 to form the cut surfaces T1 and T2. Thus, if the cut surfaces S1, S2 and T1, T2 are formed on both sides of the gears 1a, 2a, the gears 1, 2 can be incorporated in the gear case G regardless of front and back.

Claims (2)

서로 맞물리는 면인 톱니면을 인볼류트곡선(involute curve)을 따라서 형성하는 동시에, 그 톱니의 선단에 설계상의 톱니끝의 두께(t0)를 확보한 한쌍의 기어를, 제로백래시(zero backlash)를 유지하여 맞물려서 이루어지는 기어펌프에 있어서, A pair of gears are formed along the involute curve along the involute curve, and the pair of gears having the design's tooth thickness (t 0 ) at the tip of the tooth are zero backlash. In the gear pump which is held and engaged, 상기 한쌍의 기어의 톱니는, 그 회전방향의 후방에 위치하는 톱니면과 톱니끝면으로 형성되는 각(角)을 커트한 후의 톱니끝의 두께(t1)를 상기 설계상의 톱니끝의 두께(t0)보다도 얇게 하고,The tooth of the pair of gears has a thickness t 1 of the tooth tip after cutting the angle formed by the tooth surface and the tooth tip surface located in the rear of the rotational direction. smaller than 0), and 상기 톱니끝의 두께(t1)는 t0-(0.07~0.35)×t0가 이루어지는 관계로 한 것을 특징으로 하는 기어펌프.Gear pump, characterized in that the relationship is (0.07 ~ 0.35) × t 0 formed - t 0 is a thickness (t 1) of said toothed end. 삭제delete
KR1020087001995A 2005-07-26 2005-07-26 Gear pump KR101237112B1 (en)

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DE102012221947A1 (en) * 2012-11-30 2014-06-05 Robert Bosch Gmbh External gear machine e.g. pump has bearing bushes that are made to correspond with receiving recesses of the housing, and gears that are formed at junctions of supplement circles on front sides of radially surrounding chamfer
ITMI20122168A1 (en) 2012-12-18 2014-06-19 Mario Antonio Morselli HYDRAULIC GEAR MACHINE AND RELATIVE TOOTHED WHEEL
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JPH11210644A (en) 1998-01-30 1999-08-03 Shimadzu Corp Gear pump motor

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US4266915A (en) * 1978-07-10 1981-05-12 Tyrone Hydraulics Inc. Gear pumps and motors
JPH112191A (en) * 1997-06-13 1999-01-06 Shimadzu Corp Gear pump or motor
DE10003735A1 (en) * 2000-01-28 2000-11-16 Bosch Gmbh Robert Mechanical hydraulic pump has meshing gear wheels with asymmetric gear tooth edges to reduce pulsation in the output pressure
CN1316162C (en) * 2003-11-24 2007-05-16 大连铁道学院 Medium-high pressure gear pump having asymmetric double-circular-arc gear shape

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Publication number Priority date Publication date Assignee Title
JPH11210644A (en) 1998-01-30 1999-08-03 Shimadzu Corp Gear pump motor

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