JP2007040133A - Reciprocating pump device - Google Patents

Reciprocating pump device Download PDF

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JP2007040133A
JP2007040133A JP2005223358A JP2005223358A JP2007040133A JP 2007040133 A JP2007040133 A JP 2007040133A JP 2005223358 A JP2005223358 A JP 2005223358A JP 2005223358 A JP2005223358 A JP 2005223358A JP 2007040133 A JP2007040133 A JP 2007040133A
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input shaft
bearing
reciprocating pump
gear
pump device
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JP4511431B2 (en
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Kazuhiro Isayama
和博 諫山
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Maruyama Manufacturing Co Ltd
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Maruyama Manufacturing Co Ltd
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Priority to TW094147045A priority patent/TW200706761A/en
Priority to CNB2006100019978A priority patent/CN100420854C/en
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Abstract

<P>PROBLEM TO BE SOLVED: To provide a reciprocating pump device capable of reducing bending stress acting on a crank shaft. <P>SOLUTION: In the reciprocating pump device 10 provided with a drive part 30 including a crank shaft driving a piston 14 of a reciprocating pump 12 and a reduction gear part 42 arranged with adjoining the drive part and including a large gear 44 attached on the crank shaft and a small gear 46 meshing with the large gear and attached to the input shaft 48 to which power is input, a first bearing 58 and a second bearing 56 rotatably supporting the input shaft are collected on a side opposite to the drive part 30 and the input shaft 48 is supported in a cantilever style. Consequently, the small gear is put close to the drive part and total length of the crank shaft is shortened to reduce bending stress. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

本発明は、往復ポンプに関し、特に、往復ポンプ装置の駆動部と減速部の構造に関する。   The present invention relates to a reciprocating pump, and more particularly, to a structure of a driving unit and a speed reducing unit of a reciprocating pump device.

往復ポンプ装置は従来から種々の型式が知られているが、背負式動力噴霧機等に用いられる往復ポンプ装置としては、下記の特許文献１に記載されているようなものがある。この往復ポンプ装置は、小型化を図るために、図３に示すように、シリンダ内でピストンを往復動させるための、クランク軸１００及びコネクションロッド１０２から構成された駆動部１０４と、この駆動部１０４にエンジン（図示しない）からの動力を減速して伝える減速部１０６とを一体的に備えている。   Various types of reciprocating pump devices have been conventionally known. As a reciprocating pump device used for a backpack type power sprayer or the like, there is one described in Patent Document 1 below. In order to reduce the size of the reciprocating pump device, as shown in FIG. 3, the reciprocating pump device includes a driving unit 104 including a crankshaft 100 and a connection rod 102 for reciprocating a piston in a cylinder, and the driving unit. 104 is integrally provided with a speed reduction unit 106 that transmits power from an engine (not shown) at a reduced speed.

駆動部１０４と減速部１０６はケーシング内に収められているが、ケーシングは、クランク軸１００を支持する軸受１０８ａ，１０８ｂの一方１０８ａを保持する軸受ケース１１０と、クランク軸１００の偏芯カム１１２を収容するクランクケース１１４と、クランク軸１００に設けられた大径の歯車１１６及びこの歯車１１６に噛合して回転を減速して伝えるピニオンギア（小径の歯車）１１８を収容するギアケース１２０と、クランク軸１００を支持するもう一方の軸受１０８ｂ、及びピニオンギア１１８が取り付けられる入力軸１２２を支持する軸受１２４ａ，１２４ｂの一方１２４ｂを保持するとともに、入力軸１２２にエンジンの出力軸を繋ぐクラッチの一部をなすドラム１２６を囲むクラッチケース１２８とから構成されている。なお、入力軸１２２を支持する他方の軸受１２４ａは、ギアケース１２０に保持される。
実用新案登録第２５４５９８５号公報 The drive unit 104 and the speed reduction unit 106 are housed in a casing. The casing includes a bearing case 110 that holds one of the bearings 108a and 108b that supports the crankshaft 100, and an eccentric cam 112 of the crankshaft 100. A crank case 114 to be accommodated, a gear 116 having a large diameter provided on the crankshaft 100, and a gear case 120 to accommodate a pinion gear (small diameter gear) 118 that meshes with the gear 116 and transmits the rotation at a reduced speed; Part of the clutch that holds the other bearing 108b that supports the shaft 100 and one of the bearings 124a and 124b that supports the input shaft 122 to which the pinion gear 118 is attached and that connects the output shaft of the engine to the input shaft 122 And a clutch case 128 surrounding the drum 126. The other bearing 124 a that supports the input shaft 122 is held by the gear case 120.
Utility Model Registration No. 2545985

上述した従来の往復ポンプ装置は、ポンプ自体が２連、直列に配されており、能力の高いものである。しかしながら、この往復ポンプ装置においては、クランク軸の軸受間が比較的長く、大きな曲げ応力がかかる可能性があると考えられる。   The conventional reciprocating pump device described above has a high capability because the pumps themselves are arranged in series in two. However, in this reciprocating pump device, the distance between the bearings of the crankshaft is relatively long, and it is considered that a large bending stress may be applied.

そこで、本発明の目的は、クランク軸にかかる曲げ応力を低減することのできる往復ポンプ装置を提供することにある。   SUMMARY OF THE INVENTION An object of the present invention is to provide a reciprocating pump device that can reduce bending stress applied to a crankshaft.

上記目的を達成するために、本発明は、往復ポンプ（１２）のピストン（１４）を駆動するクランク軸（３２）を有する駆動部（３０）と、この駆動部（３０）に隣接して配置され、クランク軸（３２）に取り付けられた大歯車（４４）、及び、大歯車（４４）と噛合し、動力が入力される入力軸（４８）に取り付けられた小歯車（４６）を有する減速部（４２）とを備える往復ポンプ装置（１０）において、入力軸（４８）を回転可能に支持する第１の軸受（５８）及び第２の軸受（６０）を駆動部（３０）とは反対の側に集め入力軸（４８）を片持ち状に支持したことを特徴としている。   In order to achieve the above object, the present invention provides a drive unit (30) having a crankshaft (32) for driving a piston (14) of a reciprocating pump (12) and a drive unit (30) adjacent to the drive unit (30). A reduction gear having a large gear (44) attached to the crankshaft (32) and a small gear (46) attached to the input shaft (48) meshing with the large gear (44) and receiving power. In the reciprocating pump device (10) including the portion (42), the first bearing (58) and the second bearing (60) that rotatably support the input shaft (48) are opposite to the drive portion (30). It is characterized in that the input shaft (48) is supported in a cantilever manner.

この構成においては、小歯車（４６）を駆動部（３０）側に寄せることができ、よって大歯車（４４）も、ピストン（１６）にコネクションロッド（３６）を介して連結されるクランク軸（３２）の偏芯カム（３４）に接近させることができる。これにより、クランク軸（３２）の全長を短くすることが可能となり、曲げ応力が低減される。   In this configuration, the small gear (46) can be moved toward the drive unit (30), and thus the large gear (44) is also connected to the piston (16) via the connection rod (36) ( 32) and the eccentric cam (34). Thereby, it becomes possible to shorten the full length of a crankshaft (32), and a bending stress is reduced.

また、本発明による往復ポンプ装置（１０）において、第１の軸受（５８）を、入力軸（４８）の軸線に垂直な方向の荷重を支持するとともに、入力軸（４８）の軸線方向に沿う小歯車（４６）から離れる方向の荷重を支持するものとし、第２の軸受（６０）を、入力軸（４８）の軸線に垂直な方向の荷重を支持するとともに、入力軸（４８）の軸線方向に沿う小歯車（４６）に向かう方向の荷重を支持するものとし、更に、減速部（４２）のケース（５２）における第１の軸受（５８）及び第２の軸受（６０）を受容する空間（６２）の内周面に凸部（６４）を設け、この凸部（６４）と小歯車（４６）との間で第１の軸受（５８）を挟持するとともに、凸部（６４）と入力軸（４８）に取り付けられるストッパ手段（５０）との間で第２の軸受（６０）を挟持するようにすることが好適である。ケース（５２）に前もって第１及び第２の軸受（５８，６０）を組み付けておくことができ、組立性が向上するからである。   In the reciprocating pump device (10) according to the present invention, the first bearing (58) supports a load in a direction perpendicular to the axis of the input shaft (48) and extends along the axial direction of the input shaft (48). The load in the direction away from the small gear (46) is supported, and the second bearing (60) supports the load in the direction perpendicular to the axis of the input shaft (48) and the axis of the input shaft (48). A load in a direction toward the small gear (46) along the direction is supported, and further, the first bearing (58) and the second bearing (60) in the case (52) of the speed reduction portion (42) are received. A convex portion (64) is provided on the inner peripheral surface of the space (62), and the first bearing (58) is sandwiched between the convex portion (64) and the small gear (46), and the convex portion (64). And the stopper means (50) attached to the input shaft (48) It is preferable to so as to sandwich a bearing (60). This is because the first and second bearings (58, 60) can be assembled in advance to the case (52), and the assemblability is improved.

上述したように、本発明によれば、入力軸（４８）を支持する２つの軸受（５８，６０）を、減速部（４２）の外側に集めて入力軸（４８）を片持ち状とすることで、小歯車（４６）を駆動部（３０）側に寄せ、それによって大歯車（４４）の位置を偏芯カム（３４）の近傍に配置させることを可能としている。これに伴い、クランク軸（３２）の両端を支持している軸受（５４，５６）間の距離が短くなり、クランク軸（３２）にかかる曲げ応力を軽減することができる。これは、軸受（５４，５６）に対する負担も軽減するものであり、往復ポンプ装置（１０）の信頼性も向上させることができる。   As described above, according to the present invention, the two bearings (58, 60) supporting the input shaft (48) are gathered outside the speed reduction portion (42) to make the input shaft (48) cantilevered. Thus, the small gear (46) is moved toward the drive unit (30), and thereby the position of the large gear (44) can be arranged in the vicinity of the eccentric cam (34). Accordingly, the distance between the bearings (54, 56) supporting both ends of the crankshaft (32) is shortened, and the bending stress applied to the crankshaft (32) can be reduced. This also reduces the burden on the bearings (54, 56), and can also improve the reliability of the reciprocating pump device (10).

また、クランク軸（３２）の短縮化に加えて、入力軸（４８）を支持する軸受（５８，６０）を片側に集めることで、従来におけるギアケースに相当する部材を省略することが可能となる。これにより、部品点数が減り、組立て作業が容易となる。また、組立て時の累積的公差が小さくなり、大歯車（４４）と小歯車（４６）との当たりの精度が向上し、軸受の耐久性向上にも寄与する。   In addition to shortening the crankshaft (32), the bearings (58, 60) that support the input shaft (48) are gathered on one side, so that members corresponding to the conventional gear case can be omitted. Become. Thereby, the number of parts is reduced and the assembling work is facilitated. Further, the cumulative tolerance at the time of assembly is reduced, the accuracy of hitting the large gear (44) and the small gear (46) is improved, and this contributes to the improvement of the durability of the bearing.

以下、本発明による往復ポンプ装置の好適な実施形態について詳細に説明する。   Hereinafter, preferred embodiments of the reciprocating pump device according to the present invention will be described in detail.

図１は、本発明による往復ポンプ装置の部分断面図であり、図２は、図１のII−II線に沿っての部分断面図である。図示の往復ポンプ装置１０は、２つの往復ポンプ１２が互いに反対向きの状態で直列に配置されている。各往復ポンプ１２は、シリンダ１４と、シリンダ１４内を往復動するピストン１６と、吐出弁１８と、吸水弁２０とを備え、ピストン１６の往復動によって吸水口２２から液体が流路２４を通り、更に流路２６を通って吐出口２８から吐出されるようになっている。各往復ポンプ１２は交互に動作するため、流路２６には間断なく液体が供給され、液体は吐出口２８から高効率で安定して吐出される。   FIG. 1 is a partial cross-sectional view of a reciprocating pump device according to the present invention, and FIG. 2 is a partial cross-sectional view taken along line II-II in FIG. In the illustrated reciprocating pump device 10, two reciprocating pumps 12 are arranged in series with their directions being opposite to each other. Each reciprocating pump 12 includes a cylinder 14, a piston 16 that reciprocates within the cylinder 14, a discharge valve 18, and a water absorption valve 20, and the liquid passes through the flow path 24 from the water inlet 22 by the reciprocating motion of the piston 16. Further, the ink is discharged from the discharge port 28 through the flow path 26. Since each reciprocating pump 12 operates alternately, the liquid is supplied to the flow path 26 without interruption, and the liquid is stably discharged from the discharge port 28 with high efficiency.

ピストン１６を駆動させるための駆動部３０は２つの往復ポンプ１２の間にあり、クランク軸３２と、クランク軸３２の偏芯カム３４に取り付けられ各往復ポンプ１２のピストン１６に接続されるコネクションロッド３６とから基本的に構成されている。クランク軸３２の偏芯カム３４とコネクションロッド３６との間には、摩耗を低減するために軸受３８が配置されている。クランク軸３２が回転すると、軸受３８及びコネクションロッド３６を介して回転運動が往復運動に変換されて、ピストン１６が往復動することとなる。クランク軸３２、コネクションロッド３６及び軸受３８は第１のケース４０内に収容されている。   The drive unit 30 for driving the piston 16 is located between the two reciprocating pumps 12 and is connected to the crankshaft 32 and the eccentric cam 34 of the crankshaft 32 and connected to the piston 16 of each reciprocating pump 12. 36 basically. A bearing 38 is disposed between the eccentric cam 34 of the crankshaft 32 and the connection rod 36 in order to reduce wear. When the crankshaft 32 rotates, the rotational motion is converted into the reciprocating motion via the bearing 38 and the connection rod 36, and the piston 16 reciprocates. The crankshaft 32, the connection rod 36 and the bearing 38 are accommodated in the first case 40.

また、クランク軸３２への動力は適当な外部駆動源、例えばエンジン（図示しない）から与えられるが、エンジンの出力軸の回転速度は高速であるため、適当な回転速度に減速してクランク軸３２に伝える減速部４２が駆動部３０に隣接して一体的に設けられている。これにより、往復ポンプ装置１０は全体として小型となり、背負式動力噴霧機等に適している。   The power to the crankshaft 32 is supplied from an appropriate external drive source, for example, an engine (not shown). Since the rotational speed of the output shaft of the engine is high, the crankshaft 32 is decelerated to an appropriate rotational speed. The speed reduction part 42 which transmits to is adjoined to the drive part 30, and is provided integrally. Thereby, the reciprocating pump apparatus 10 becomes small as a whole, and is suitable for a backpack type power sprayer or the like.

減速部４２は、クランク軸３２に取り付けられた大歯車４４と、この大歯車４４に噛合するピニオンギア（小歯車）４６とを備えている。ピニオンギア４６は、エンジンからの動力が入力される入力軸４８に取り付けられ、この入力軸４８の外側端部にはドラム（ストッパ手段）５０と称されるクラッチ機構の一部が取り付けられている。クラッチ機構は、エンジンの出力軸の回転駆動力を断接可能に入力軸４８に伝えるものである。減速部４２はこのような構成となっているので、エンジンにより高速の回転が入力軸４８に伝えられると、その回転は歯数の少ないピニオンギア４６から、より歯数の多い大歯車４４に伝えられて所望の回転速度に減速される。   The speed reduction unit 42 includes a large gear 44 attached to the crankshaft 32 and a pinion gear (small gear) 46 that meshes with the large gear 44. The pinion gear 46 is attached to an input shaft 48 to which power from the engine is input, and a part of a clutch mechanism called a drum (stopper means) 50 is attached to an outer end portion of the input shaft 48. . The clutch mechanism transmits the rotational driving force of the output shaft of the engine to the input shaft 48 so that it can be connected and disconnected. Since the speed reducing portion 42 has such a configuration, when a high speed rotation is transmitted to the input shaft 48 by the engine, the rotation is transmitted from the pinion gear 46 having a smaller number of teeth to the large gear 44 having a larger number of teeth. And decelerated to a desired rotational speed.

減速部４２の大歯車４４及びピニオンギア４６は、第１のケース４０と、これに結合される第２のケース５２との間に空間に収容され、また、入力軸４８及びドラム５０は第２のケース５２内に収められる。   The large gear 44 and the pinion gear 46 of the speed reduction portion 42 are accommodated in a space between the first case 40 and the second case 52 coupled thereto, and the input shaft 48 and the drum 50 are the second. In the case 52.

クランク軸３２の両端部は軸受５４，５６により回転可能に支持されている。一方の軸受５４は第１のケース４０に保持され、他方の軸受５６は第２のケース５２により保持されている。   Both ends of the crankshaft 32 are rotatably supported by bearings 54 and 56. One bearing 54 is held by the first case 40, and the other bearing 56 is held by the second case 52.

一方、入力軸４８の駆動部３０側の端部には軸受はなく、ピニオンギア４６が取り付けられている。そして、入力軸４８を支持するための第１及び第２の軸受５８，６０が、ピニオンギア４６から、駆動部３０とは反対側に延びる部分に並設され、入力軸４８を片持ち状に支持している。   On the other hand, there is no bearing at the end of the input shaft 48 on the drive unit 30 side, and a pinion gear 46 is attached. And the 1st and 2nd bearings 58 and 60 for supporting the input shaft 48 are arranged in parallel by the part extended on the opposite side to the drive part 30 from the pinion gear 46, and the input shaft 48 is cantilevered. I support it.

第１及び第２の軸受５８，６０は、第２のケース５２に形成された円筒状の空間６２に受容される。この空間６２の内周面には環状の凸部６４が形成されており、この凸部６４を挟むようにして第１及び第２の軸受５８，６０が配置されている。更に、これらの軸受５８，６０は、ピニオンギア４６とドラム５０とによって挟持され、空間６２から脱落しないようになっている。   The first and second bearings 58 and 60 are received in a cylindrical space 62 formed in the second case 52. An annular convex portion 64 is formed on the inner peripheral surface of the space 62, and the first and second bearings 58 and 60 are arranged so as to sandwich the convex portion 64. Further, these bearings 58 and 60 are sandwiched between the pinion gear 46 and the drum 50 so as not to drop out of the space 62.

本実施形態においては、第１及び第２の軸受５８，６０は共に玉軸受であり、入力軸４８の軸線に垂直な方向の荷重（ラジアル荷重）と、入力軸４８の軸線に沿う方向の荷重（スラスト荷重）とを支持することができる、いわゆるラジアル・スラスト型である。第１の軸受５８に関しては、入力軸４８に駆動部３０とは反対側への荷重、すなわち外側に向かうスラスト荷重が作用した場合、これを支持できるよう、その向きが定められ、凸部６４とピニオンギア４６との間で挟持される。一方、第２の軸受６０は、入力軸４８に駆動部３０側への荷重、すなわちピニオンギア４６に向かうスラスト荷重が作用した場合、これを支持できるよう、第１の軸受５８とは反対向きとされ、凸部６４とドラム５０との間で挟持される。かかる構成により、入力軸４８は、その軸線に沿う両方向のスラスト荷重と、径方向のラジアル荷重とに関し、確実に支持されることとなる。   In the present embodiment, the first and second bearings 58 and 60 are both ball bearings, and a load in the direction perpendicular to the axis of the input shaft 48 (radial load) and a load in the direction along the axis of the input shaft 48 are used. It is a so-called radial thrust type that can support (thrust load). With respect to the first bearing 58, when a load on the input shaft 48 opposite to the drive unit 30, that is, a thrust load toward the outside, is applied, its direction is determined so that it can be supported. It is clamped between the pinion gear 46. On the other hand, the second bearing 60 has a direction opposite to that of the first bearing 58 so that it can support the input shaft 48 when a load on the drive unit 30 side, that is, a thrust load toward the pinion gear 46 acts. And is sandwiched between the convex portion 64 and the drum 50. With this configuration, the input shaft 48 is reliably supported with respect to the thrust load in both directions along the axis and the radial load in the radial direction.

なお、入力軸４８の回転が妨げられないように、凸部６４は第１及び軸受５８，６０の外レースのみに接し、ピニオンギア４６は第１の軸受５８の内レースのみ、ドラム５０は第２の軸受６０の内レースのみに接する。   In order to prevent the rotation of the input shaft 48 from being disturbed, the convex portion 64 contacts only the first and outer races of the bearings 58, 60, the pinion gear 46 only the inner race of the first bearing 58, and the drum 50 the first. It contacts only the inner race of the second bearing 60.

上述したような構成においては、第１及び第２の軸受５８，６０を入力軸４８の片側に集めたため、入力軸４８の駆動部３０側の端部がピニオンギア４６から突出させないですむ。このため、ピニオンギア４６を駆動部３０側に近づけることが可能となる。よって、ピニオンギア４６に噛合する大歯車４４を偏芯カム３４に接近させることができ、ひいてはクランク軸３２の全長を短くすることが可能となる。これは、図１と従来構成の図３とを比較することで容易に理解されよう。クランク軸３２は、その両端が軸受５４，５６で支持されているが、軸受５４，５６間の距離も短くなることから、クランク軸３２に作用する径方向の力による曲げ応力を低減することが可能となる。勿論、軸受５４，５６に作用する反力も低減される。従って、クランク軸３２及び軸受５４，５６の耐久性が向上し、往復ポンプ装置１０の信頼性が向上するとともに、寿命も延びる。   In the configuration as described above, since the first and second bearings 58 and 60 are gathered on one side of the input shaft 48, the end of the input shaft 48 on the drive unit 30 side does not need to protrude from the pinion gear 46. Therefore, the pinion gear 46 can be brought closer to the drive unit 30 side. Therefore, the large gear 44 meshing with the pinion gear 46 can be brought close to the eccentric cam 34, and the overall length of the crankshaft 32 can be shortened. This can be easily understood by comparing FIG. 1 with FIG. 3 of the conventional configuration. Although both ends of the crankshaft 32 are supported by the bearings 54 and 56, the distance between the bearings 54 and 56 is also shortened, so that the bending stress due to the radial force acting on the crankshaft 32 can be reduced. It becomes possible. Of course, the reaction force acting on the bearings 54 and 56 is also reduced. Accordingly, the durability of the crankshaft 32 and the bearings 54 and 56 is improved, the reliability of the reciprocating pump device 10 is improved, and the life is extended.

また、上記構成においては、入力軸４８を支持する第１及び第２の軸受５８，６０を片側に集め、ピニオンギア４６とドラム５０とで挟持させることとしているため、第２のケース５２にピニオンギア４６、第１及び第２の軸受５８，６０、入力軸４８及びドラム５０を予め組み付けておくことができる。このため、本実施形態では、図１から理解されるように、２つのケース４０，５２のみで駆動部３０と減速部４２を収めることが可能となる。従来においては、図３に示すように入力軸１２２の両端に軸受１２４ａ，１２４ｂを取り付けることとしていたため、駆動部１０４側となる軸受１２４ａを保持するためのケース（ギアケース）１２０を別個に用意しておく必要があり、組立工程も多く手間がかかることは勿論、組付部品点数が多いことによる累積的公差が大きくなるという問題点があったが、本実施形態ではかかる問題点はない。よって、大歯車４４とピニオンギア４６との間の精度も出しやすく、その結果、大歯車４４やピニオンギア４６、軸受５４，５６，５８，６０の耐久性の向上にも寄与する。このこともまた、往復ポンプ装置１０の信頼性向上等に資するものである。   In the above configuration, the first and second bearings 58 and 60 that support the input shaft 48 are gathered on one side and sandwiched between the pinion gear 46 and the drum 50, so that the second case 52 has a pinion. The gear 46, the first and second bearings 58 and 60, the input shaft 48, and the drum 50 can be assembled in advance. Therefore, in this embodiment, as can be understood from FIG. 1, the drive unit 30 and the speed reduction unit 42 can be accommodated by only the two cases 40 and 52. Conventionally, since bearings 124a and 124b are attached to both ends of the input shaft 122 as shown in FIG. 3, a case (gear case) 120 for holding the bearing 124a on the drive unit 104 side is prepared separately. In addition, there is a problem that the cumulative tolerance is increased due to a large number of parts to be assembled, as well as a lot of time and labor for the assembly process, but this embodiment does not have such a problem. Therefore, the accuracy between the large gear 44 and the pinion gear 46 can be easily obtained, and as a result, the durability of the large gear 44, the pinion gear 46, and the bearings 54, 56, 58, 60 is also improved. This also contributes to improving the reliability of the reciprocating pump device 10.

以上、本発明の好適な実施形態について詳細に説明したが、本発明は上記実施形態に限られないことはいうまでもない。例えば、上記実施形態では、第１及び第２の軸受５８，６０をドラム５０で固定することとしているが、軸受固定専用のリングのようなストッパ手段を入力軸４８に取り付けてもよい。また、往復ポンプが１つだけ、或いは、３つ以上備える往復ポンプ装置にも本発明は適用可能である。   As mentioned above, although preferred embodiment of this invention was described in detail, it cannot be overemphasized that this invention is not restricted to the said embodiment. For example, in the above embodiment, the first and second bearings 58 and 60 are fixed by the drum 50, but stopper means such as a ring dedicated to fixing the bearing may be attached to the input shaft 48. The present invention is also applicable to a reciprocating pump device having only one reciprocating pump or three or more reciprocating pumps.

本発明による往復ポンプ装置の一実施形態を示す部分断面図である。It is a fragmentary sectional view showing one embodiment of a reciprocating pump device by the present invention. 図１のII−II線に沿っての部分断面図である。It is a fragmentary sectional view along the II-II line of FIG. 従来の往復ポンプ装置を示す部分断面図である。It is a fragmentary sectional view which shows the conventional reciprocating pump apparatus.

符号の説明Explanation of symbols

１０…往復ポンプ装置、１２…往復ポンプ、１４…シリンダ、１６…ピストン、３０…駆動部、３２…クランク軸、３４…偏芯カム、３６…コネクションロッド、４０…第１のケース、４２…減速部、４４…大歯車、４６…ピニオンギア（小歯車）、４８…入力軸、５０…ドラム（環状体）、５２…第２のケース、５８…第１の軸受、６０…第２の軸受、６２…空間、６４…凸部。
DESCRIPTION OF SYMBOLS 10 ... Reciprocating pump apparatus, 12 ... Reciprocating pump, 14 ... Cylinder, 16 ... Piston, 30 ... Drive part, 32 ... Crankshaft, 34 ... Eccentric cam, 36 ... Connection rod, 40 ... First case, 42 ... Deceleration , 44 ... large gear, 46 ... pinion gear (small gear), 48 ... input shaft, 50 ... drum (annular body), 52 ... second case, 58 ... first bearing, 60 ... second bearing, 62 ... space, 64 ... convex.

Claims (2)

往復ポンプ（１２）のピストン（１４）を駆動するクランク軸（３２）を有する駆動部（３０）と、前記駆動部（３０）に隣接して配置され、前記クランク軸（３２）に取り付けられた大歯車（４４）、及び、前記大歯車（４４）と噛合し、動力が入力される入力軸（４８）に取り付けられた小歯車（４６）を有する減速部（４２）とを備える往復ポンプ装置（１０）において、
前記入力軸（４８）を回転可能に支持する第１の軸受（５８）及び第２の軸受（６０）を前記駆動部（３０）とは反対の側に集め前記入力軸（４８）を片持ち状に支持したことを特徴とする、往復ポンプ装置。 A drive unit (30) having a crankshaft (32) for driving a piston (14) of a reciprocating pump (12), and disposed adjacent to the drive unit (30) and attached to the crankshaft (32) A reciprocating pump device comprising: a large gear (44); and a reduction gear (42) having a small gear (46) which is engaged with the large gear (44) and attached to an input shaft (48) to which power is input. In (10),
The first bearing (58) and the second bearing (60) that rotatably support the input shaft (48) are collected on the side opposite to the drive unit (30), and the input shaft (48) is cantilevered. A reciprocating pump device characterized by being supported in a shape. 前記第１の軸受（５８）は、前記入力軸（４８）の軸線に垂直な方向の荷重を支持するとともに、前記入力軸（４８）の軸線方向に沿う前記小歯車（４６）から離れる方向の荷重を支持するものであり、
前記第２の軸受（６０）は、前記入力軸（４８）の軸線に垂直な方向の荷重を支持するとともに、前記入力軸（４８）の軸線方向に沿う前記小歯車（４６）に向かう方向の荷重を支持するものであり、
前記減速部（４２）のケース（５２）における前記第１の軸受（５８）及び前記第２の軸受（６０）を受容する空間（６２）の内周面に凸部（６４）を設け、前記凸部（６４）と前記小歯車（４６）との間で第１の軸受（５８）を挟持するとともに、前記凸部（６４）と前記入力軸（４８）に取り付けられるストッパ手段（５０）との間で前記第２の軸受（６０）を挟持するようにしたことを特徴とする、請求項１に記載の往復ポンプ装置。
The first bearing (58) supports a load in a direction perpendicular to the axis of the input shaft (48) and moves away from the small gear (46) along the axial direction of the input shaft (48). To support the load,
The second bearing (60) supports a load in a direction perpendicular to the axis of the input shaft (48) and is directed to the small gear (46) along the axial direction of the input shaft (48). To support the load,
Protruding portions (64) are provided on the inner peripheral surface of the space (62) for receiving the first bearing (58) and the second bearing (60) in the case (52) of the speed reduction portion (42), The first bearing (58) is sandwiched between a convex portion (64) and the small gear (46), and stopper means (50) attached to the convex portion (64) and the input shaft (48). The reciprocating pump device according to claim 1, characterized in that the second bearing (60) is sandwiched between them.
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