WO2013005703A1 - Swash plate type hydraulic motor and swash plate type hydraulic pump - Google Patents
Swash plate type hydraulic motor and swash plate type hydraulic pump Download PDFInfo
- Publication number
- WO2013005703A1 WO2013005703A1 PCT/JP2012/066841 JP2012066841W WO2013005703A1 WO 2013005703 A1 WO2013005703 A1 WO 2013005703A1 JP 2012066841 W JP2012066841 W JP 2012066841W WO 2013005703 A1 WO2013005703 A1 WO 2013005703A1
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- Prior art keywords
- swash plate
- type hydraulic
- plate type
- piston
- hydraulic motor
- Prior art date
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Classifications
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- 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
- F04B1/2078—Swash plates
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
- F03C1/00—Reciprocating-piston liquid engines
- F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
- F03C1/06—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis
- F03C1/061—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
- F03C1/0623—Details, component parts
- F03C1/0631—Wobbler or actuated element
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
- F03C1/00—Reciprocating-piston liquid engines
- F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
- F03C1/06—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis
- F03C1/0636—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
- F03C1/0644—Component parts
- F03C1/0668—Swash or actuated plate
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- 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
- F04B1/14—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 stationary cylinders
- F04B1/141—Details or component parts
- F04B1/146—Swash plates; Actuating elements
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- 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
- F04B1/2078—Swash plates
- F04B1/2085—Bearings for swash plates or driving axles
Definitions
- the present invention relates to a swash plate type hydraulic motor or a swash plate type hydraulic pump used in construction vehicles such as a hydraulic excavator.
- the swash plate type hydraulic motor or swash plate type hydraulic pump has a tilting piston for changing the tilt angle of the swash plate.
- the swash plate (12) and the tilt control piston (14B) are in point contact.
- the present invention has been made in view of the above problems, and an object of the present invention is to provide a swash plate having a structure capable of preventing wear and cracking of the swash plate without subjecting the swash plate to a hardening treatment such as heat treatment. It is to provide a plate type hydraulic motor or a swash plate type hydraulic pump.
- the present invention for solving the above problems includes a main body case, a rotating shaft housed in the main body case, a cylinder block attached to the rotating shaft, and a plurality of cylinder holes formed in the cylinder block.
- a piston slidably inserted into the cylinder hole, a shoe provided at the tip of the piston, a slope on which the shoe slides, and formed on the opposite side of the slope to support the body case
- a swash plate a tilting piston that abuts the support surface of the swash plate and tilts the swash plate by pressing the swash plate toward the piston
- the main body In a swash plate type hydraulic motor or swash plate type hydraulic pump, which is formed in a case and includes a tilt piston cylinder hole into which the tilt piston is slidably inserted, a swash plate side end of the tilt piston
- the spherical portion is integrally formed with the concave portion having the same shape as the spherical portion into which the spherical portion is
- the swash plate and the tilting piston come into contact with each other via the plate member.
- the contact area between the tilting piston and the plate member, and the contact area between the plate member and the swash plate both increase compared to the contact area between the conventional swash plate and the tilting piston. It is not a concentrated load as in the past. Therefore, it is possible to prevent the swash plate from being worn or cracked without subjecting the swash plate to a curing treatment such as heat treatment.
- the plate member is disposed closer to the swash plate than the opening side end surface of the tilting piston cylinder hole.
- the axial length of the tilting piston can be made the same as the conventional length, and uneven wear of the tilting piston cylinder hole due to the tilting piston tilting can be prevented.
- the area of the sliding surface of the plate member is larger than the area of the cylinder hole for the tilting piston.
- the plate member since the pressure receiving area of the plate member increases and the surface pressure decreases, the plate member can be manufactured using an inexpensive material.
- the spherical portion is integrally formed on the end surface of the tilting piston on the swash plate side, and the concave portion having the same shape as the spherical portion into which the spherical portion is slidably fitted is provided on the tilting piston side.
- a plate member having a sliding surface on the swash plate side that slides with the support surface of the swash plate is disposed between the swash plate and the tilting piston, so that the swash plate is not subjected to hardening treatment such as heat treatment.
- a swash plate type hydraulic motor or a swash plate type hydraulic pump having a structure capable of preventing wear and cracking of the swash plate can be provided.
- a swash plate type hydraulic motor 1 (swash plate type hydraulic rotating machine) described below is used for a traveling device in a construction vehicle such as a hydraulic excavator, and is capable of switching between two speeds of high speed and low speed.
- Type hydraulic motor The present invention can be applied not only to a swash plate type hydraulic motor but also to a swash plate type hydraulic pump.
- FIG. 1 and 3 are sectional views of a swash plate type hydraulic motor 1 according to an embodiment of the present invention.
- FIG. 1 is a view when the swash plate 7 is at a low speed position, and FIG. It is a figure when there is.
- FIG. 2 is an enlarged view of part A in FIG.
- the hydraulic motor 1 includes a main body case 2, a rotating shaft 3, a cylinder block 4, a piston 5, a shoe 6, a swash plate 7, a tilting piston 8, and the like.
- the main body case 2 is for housing the rotary shaft 3, the cylinder block 4, the piston 5, the swash plate 7 and the like, and the rotary shaft 3 is held rotatably with respect to the main body case 2.
- the cylinder block 4 is spline-coupled to the rotating shaft 3 and is attached to the rotating shaft 3 so as to be movable in the axial direction X of the rotating shaft 3 and to rotate together with the rotating shaft 3 in the rotating direction of the rotating shaft 3. ing.
- a plurality of cylinder holes 4 a are formed in the axial direction around the axis of the cylinder block 4. These cylinder holes 4a are arranged at equal intervals on the same circumference.
- the cylinder hole 4 a is formed in the cylinder block 4 so that its longitudinal direction is parallel to the axial direction X.
- Plural pistons 5 are provided, and are inserted into the cylinder holes 4a so as to be slidable with respect to the inner wall surface of the cylinder hole 4a.
- a shoe 6 is attached to a sphere formed at the tip of the piston 5.
- the swash plate 7 has an inclined surface 7 a on which the shoe 6 slides, and a support surface 7 b that is formed on the opposite side of the inclined surface 7 a and is supported with respect to the main body case 2.
- the swash plate 7 is formed in an annular shape when viewed from the axial direction X, and the rotating shaft 3 passes therethrough.
- each cylinder hole 4a of the cylinder block 4 When the pressure oil is supplied to and discharged from each cylinder hole 4a of the cylinder block 4, the piston 5 inserted into each cylinder hole 4a reciprocates. As the piston 5 reciprocates, the shoe 6 rotates while sliding on the inclined surface 7a of the swash plate 7, and the piston 5 also rotates. The cylinder block 4 is rotated by the rotation of the piston 5, and the rotating shaft 3 is rotated integrally with the cylinder block 4.
- the support surface 7b of the swash plate 7 includes a first support surface 7b1 and a second support surface 7b2 which are two surfaces having different angles with respect to the axial direction X of the rotary shaft 3.
- Pivots 11 are slidably disposed on the support surface 7b of the swash plate 7 on both sides of the rotary shaft 3 on the intersecting line where the first support surface 7b1 and the second support surface 7b2 intersect. These two pivots 11 are fixed to the main body case 2.
- the swash plate 7 has two pivots between a position where the first support surface 7b1 contacts the main body case 2 (see FIG. 3) and a position where the second support surface 7b2 contacts the main body case 2 (see FIG. 1). 11 is used as a fulcrum.
- tilt piston On the inner wall surface of the main body case 2 where the second support surface 7b2 of the swash plate 7 comes into contact with the main body case 2, there is provided a tilt piston cylinder hole 9 having a circular cross section into which the tilt piston 8 is slidably inserted. It has been.
- a tilting piston 8 that tilts (swings) the swash plate 7 by inserting the swash plate 7 toward the piston 5 is inserted into the tilting piston cylinder hole 9.
- the tilting piston 8 has a cylindrical body 8a that slides on the inner wall surface of the tilting piston cylinder hole 9, and the main body 8a on the end face of the main body 8a on the swash plate 7 side. And a spherical portion 8b formed integrally with the portion 8a.
- integrally formed means that the tilting piston 8 having the main body portion 8a and the spherical surface portion 8b is manufactured from one material by casting, cutting, or the like. This means that the main body portion 8a and the spherical surface portion 8b are not separately manufactured parts.
- a back pressure chamber 13 into which pressure oil for operating the tilting piston 8 is introduced is formed between the end of the main body 8a opposite to the spherical surface 8b and the bottom surface of the tilting piston cylinder hole 9. Yes.
- the pressure oil to the back pressure chamber 13 for operating the tilting piston 8 is supplied through an oil passage 14 provided in the main body case 2.
- the tilting piston 8 is always urged toward the swash plate 7 by a coil spring 12 disposed in the back pressure chamber 13.
- the tilting piston 8 presses the swash plate 7 toward the piston 5 side by switching a switching valve (not shown) and supplying pressure oil to the back pressure chamber 13 through the oil passage 14. ing.
- the tilt angle of the swash plate 7 changes and the hydraulic motor 1 switches from high speed to low speed (see FIG. 1).
- the oil escapes from the back pressure chamber 13 and the tilting piston 8 moves backward, and the tilting angle of the swash plate 7 changes to switch the hydraulic motor 1 from low to high. (See FIG. 3).
- a plate member 10 is disposed between the swash plate 7 and the tilting piston 8.
- the plate member 10 includes a concave portion 10a having the same shape as the spherical portion 8b into which the spherical portion 8b of the tilting piston 8 is slidably fitted, and a second support surface 7b2 formed on the second support surface 7b2 of the swash plate 7. It is a disk-shaped member which has the circular recessed part 7c which is a part, and the flat sliding surface 10b which slides. The outer peripheral edge of the sliding surface 10b is chamfered 10c.
- the spherical surface portion 8b of the tilting piston 8 and the concave portion 10a of the plate member 10, and the sliding surface 10b of the plate member 10 and the concave portion 7c of the swash plate 7 are all formed in surface contact.
- the diameter D1 of the plate member 10 is smaller than the diameter D2 of the cylinder hole 9 for the tilting piston.
- the plate member 10 when the swash plate 7 is at the low speed position, the plate member 10 is disposed on the swash plate 7 side of the opening side end surface of the tilting piston cylinder hole 9.
- the depth of the circular recess 7c that is a part of the second support surface 7b2 is equal to the thickness of the plate member 10. That is, the second support surface 7b2 (a position that is not the recess 7c) of the swash plate 7 and the plate member 10 are flush with each other.
- the inner diameter of the concave portion 7 c of the second support surface 7 b 2 is made larger than the diameter D 1 of the plate member 10. That is, there is a gap between the plate member 10 and the recess 7c, and the plate member 10 is movable in the recess 7c while being in contact with the bottom surface of the recess 7c.
- the plate member 10 that is easy to manufacture is simply sandwiched between the swash plate 7 and the tilting piston 8, and the swash plate 7 is worn without being subjected to a hardening process such as heat treatment. -It can prevent cracking. Further, since the plate member 10 is movable in the recess 7c while being in contact with the bottom surface of the recess 7c of the swash plate 7, the spherical portion 8b of the tilting piston 8 and the recess 10a of the plate member 10 that are in contact with each other. The relative deviation between the two is less likely to occur. Therefore, wear of the spherical surface portion 8b and the concave portion 10a is unlikely to occur.
- the tilt piston 8 since the swash plate 7 and the plate member 10 wrap in the axial direction X, even if the plate member 10 is disposed between the swash plate 7 and the tilt piston 8, the tilt piston 8 It is not necessary to make the axial length shorter than before. That is, the axial length of the tilting piston 8 can be made the same as that of the conventional one, and uneven wear of the tilting piston cylinder hole 9 due to the tilting of the tilting piston 8 can be prevented. In addition, from another viewpoint, there is an effect that the axial length of the hydraulic motor 1 does not need to be longer than that in the related art.
- the diameter D1 of the plate member 10 is smaller than the diameter D2 of the tilting piston cylinder hole 9, but the diameter D1 of the plate member 10 is set to the diameter D2 of the tilting piston cylinder hole 9. It is also preferable to make it larger. That is, it is also preferable that the area of the sliding surface 10 b of the plate member 10 is larger than the area of the tilting piston cylinder hole 9. By doing in this way, since the pressure receiving area of the plate member 10 becomes large and a surface pressure falls, it becomes possible to manufacture the plate member 10 using an inexpensive metal raw material.
- the plate member 10 may not be disk shape, for example, elliptical plate shape etc. may be sufficient.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Hydraulic Motors (AREA)
- Reciprocating Pumps (AREA)
Abstract
The objective of the present invention is to provide a swash plate type hydraulic motor and a swash plate type hydraulic pump having a construction with which abrasion/cracking of the swash plate can be prevented, without applying a hardening process such as thermal processing to the swash plate.
One embodiment of the present invention is a swash plate type hydraulic motor (1). A spherical surface part (8b) is formed integrally on the swash-plate-side end face of a tilting piston (8). A plate member (10), which has a concave part (10a) on the tilting-piston side having the same shape as the spherical surface part (8b) and into which the spherical surface part (8b) fits in a slidable manner, and a sliding surface (10b) on the swash-plate side that slides on a second support surface (7b2), is arranged between the swash plate (7) and the tilting piston (8).
Description
本発明は、油圧ショベルなどの建設車両に用いられる斜板式油圧モータ又は斜板式油圧ポンプに関する。
The present invention relates to a swash plate type hydraulic motor or a swash plate type hydraulic pump used in construction vehicles such as a hydraulic excavator.
斜板式油圧モータ又は斜板式油圧ポンプは、斜板の傾転角度を変化させるための傾転ピストンを有する。ここで、例えば特許文献1に記載された斜板式油圧モータ(1)では、斜板(12)と傾転制御ピストン(14B)とが点接触している。
The swash plate type hydraulic motor or swash plate type hydraulic pump has a tilting piston for changing the tilt angle of the swash plate. Here, for example, in the swash plate hydraulic motor (1) described in Patent Document 1, the swash plate (12) and the tilt control piston (14B) are in point contact.
特許文献1に記載のように、斜板(12)と傾転制御ピストン(14B)とが点接触していると、斜板(12)が磨耗したり、割れたりすることがある。斜板(12)の摩耗・割れを防止するためには、斜板(12)に熱処理を施す対応が考えられるが、熱処理の追加は高価である。
As described in Patent Document 1, when the swash plate (12) and the tilt control piston (14B) are in point contact, the swash plate (12) may be worn or cracked. In order to prevent wear and cracking of the swash plate (12), it is possible to apply heat treatment to the swash plate (12), but the addition of heat treatment is expensive.
本発明は、上記課題に鑑みてなされたものであって、その目的は、熱処理などの硬化処理を斜板に施すことなく、斜板の摩耗・割れを防止することができる構造を備えた斜板式油圧モータ又は斜板式油圧ポンプを提供することである。
The present invention has been made in view of the above problems, and an object of the present invention is to provide a swash plate having a structure capable of preventing wear and cracking of the swash plate without subjecting the swash plate to a hardening treatment such as heat treatment. It is to provide a plate type hydraulic motor or a swash plate type hydraulic pump.
上記課題を解決するための本発明は、本体ケースと、前記本体ケース内に収納された回転軸と、前記回転軸に取り付けられたシリンダブロックと、前記シリンダブロックに形成された複数のシリンダ穴と、前記シリンダ穴に摺動自在に挿入されたピストンと、前記ピストンの先端に設けられたシューと、前記シューが摺動する斜面と、当該斜面の反対側に形成され前記本体ケースに対して支持される支持面と、を有する斜板と、前記斜板の支持面に当接し、当該斜板を前記ピストン側に向かって押圧することで当該斜板を傾転させる傾転ピストンと、前記本体ケースに形成され前記傾転ピストンが摺動自在に挿入される傾転ピストン用シリンダ穴と、を備える斜板式油圧モータ又は斜板式油圧ポンプにおいて、前記傾転ピストンの斜板側端面に球面部が一体的に形成されており、傾転ピストン側に前記球面部が摺動自在に嵌り込む当該球面部と同形状の凹部と、斜板側に前記支持面と摺動する摺動面と、を有するプレート部材が、前記斜板と前記傾転ピストンとの間に配置されていることを特徴とする斜板式油圧モータ又は斜板式油圧ポンプである。
The present invention for solving the above problems includes a main body case, a rotating shaft housed in the main body case, a cylinder block attached to the rotating shaft, and a plurality of cylinder holes formed in the cylinder block. , A piston slidably inserted into the cylinder hole, a shoe provided at the tip of the piston, a slope on which the shoe slides, and formed on the opposite side of the slope to support the body case A swash plate, a tilting piston that abuts the support surface of the swash plate and tilts the swash plate by pressing the swash plate toward the piston, and the main body In a swash plate type hydraulic motor or swash plate type hydraulic pump, which is formed in a case and includes a tilt piston cylinder hole into which the tilt piston is slidably inserted, a swash plate side end of the tilt piston The spherical portion is integrally formed with the concave portion having the same shape as the spherical portion into which the spherical portion is slidably fitted on the tilting piston side, and the sliding slide with the support surface on the swash plate side. A swash plate type hydraulic motor or a swash plate type hydraulic pump characterized in that a plate member having a surface is disposed between the swash plate and the tilting piston.
この構成によれば、斜板と傾転ピストンとがプレート部材を介して当接する。傾転ピストンとプレート部材との接触面積、およびプレート部材と斜板との接触面積は、いずれも従来の斜板と傾転ピストンとの接触面積に比べて増加するので傾転ピストンの押圧力は従来のような集中荷重とはならない。したがって、熱処理などの硬化処理を斜板に施すことなく、斜板の摩耗・割れを防止することができる。
According to this configuration, the swash plate and the tilting piston come into contact with each other via the plate member. The contact area between the tilting piston and the plate member, and the contact area between the plate member and the swash plate both increase compared to the contact area between the conventional swash plate and the tilting piston. It is not a concentrated load as in the past. Therefore, it is possible to prevent the swash plate from being worn or cracked without subjecting the swash plate to a curing treatment such as heat treatment.
また本発明において、前記斜板が低速位置にあるときに、前記傾転ピストン用シリンダ穴の開口側端面よりも斜板側に前記プレート部材が配置されていることが好ましい。
In the present invention, it is preferable that when the swash plate is at a low speed position, the plate member is disposed closer to the swash plate than the opening side end surface of the tilting piston cylinder hole.
この構成によれば、斜板と傾転ピストンとの間にプレート部材を配置したとしても、傾転ピストンの軸方向長さを従来よりも短くする必要がない。すなわち、傾転ピストンの軸方向長さを従来と同様の長さとすることができ、傾転ピストンが傾くことに起因する傾転ピストン用シリンダ穴の偏摩耗を防止できる。
According to this configuration, even if a plate member is disposed between the swash plate and the tilting piston, it is not necessary to make the axial length of the tilting piston shorter than in the past. That is, the axial length of the tilting piston can be made the same as the conventional length, and uneven wear of the tilting piston cylinder hole due to the tilting piston tilting can be prevented.
さらに本発明において、前記プレート部材の摺動面の面積が、前記傾転ピストン用シリンダ穴の面積よりも大きくされていることが好ましい。
Furthermore, in the present invention, it is preferable that the area of the sliding surface of the plate member is larger than the area of the cylinder hole for the tilting piston.
この構成によれば、プレート部材の受圧面積が大きくなり面圧が下がるので、安価な素材を用いてプレート部材を製作することが可能となる。
According to this configuration, since the pressure receiving area of the plate member increases and the surface pressure decreases, the plate member can be manufactured using an inexpensive material.
本発明によれば、傾転ピストンの斜板側端面に球面部を一体的に形成するとともに、この球面部が摺動自在に嵌り込む当該球面部と同形状の凹部を傾転ピストン側に、斜板の支持面と摺動する摺動面を斜板側に有するプレート部材を、斜板と傾転ピストンとの間に配置することで、熱処理などの硬化処理を斜板に施すことなく、斜板の摩耗・割れを防止することができる構造を備えた斜板式油圧モータ又は斜板式油圧ポンプとすることができる。
According to the present invention, the spherical portion is integrally formed on the end surface of the tilting piston on the swash plate side, and the concave portion having the same shape as the spherical portion into which the spherical portion is slidably fitted is provided on the tilting piston side. A plate member having a sliding surface on the swash plate side that slides with the support surface of the swash plate is disposed between the swash plate and the tilting piston, so that the swash plate is not subjected to hardening treatment such as heat treatment. A swash plate type hydraulic motor or a swash plate type hydraulic pump having a structure capable of preventing wear and cracking of the swash plate can be provided.
以下、本発明を実施するための形態について図面を参照しつつ説明する。以下に説明する斜板式の油圧モータ1(斜板式油圧回転機)は、油圧ショベルなどの建設車両における走行装置に用いられるものであって、高速と低速との2速切換えを可能とする可変容量型の油圧モータである。なお、本発明は、斜板式油圧モータだけでなく斜板式油圧ポンプにも適用することができる。
Hereinafter, embodiments for carrying out the present invention will be described with reference to the drawings. A swash plate type hydraulic motor 1 (swash plate type hydraulic rotating machine) described below is used for a traveling device in a construction vehicle such as a hydraulic excavator, and is capable of switching between two speeds of high speed and low speed. Type hydraulic motor. The present invention can be applied not only to a swash plate type hydraulic motor but also to a swash plate type hydraulic pump.
(斜板式油圧モータの構成)
図1、3は、本発明の一実施形態に係る斜板式の油圧モータ1の断面図であり、図1は斜板7が低速位置にあるときの図、図3は斜板7が高速位置にあるときの図である。図2は、図1のA部拡大図である。 (Configuration of swash plate hydraulic motor)
1 and 3 are sectional views of a swash plate typehydraulic motor 1 according to an embodiment of the present invention. FIG. 1 is a view when the swash plate 7 is at a low speed position, and FIG. It is a figure when there is. FIG. 2 is an enlarged view of part A in FIG.
図1、3は、本発明の一実施形態に係る斜板式の油圧モータ1の断面図であり、図1は斜板7が低速位置にあるときの図、図3は斜板7が高速位置にあるときの図である。図2は、図1のA部拡大図である。 (Configuration of swash plate hydraulic motor)
1 and 3 are sectional views of a swash plate type
図1~3に示すように、油圧モータ1は、本体ケース2、回転軸3、シリンダブロック4、ピストン5、シュー6、斜板7、傾転ピストン8などを備えている。
1-3, the hydraulic motor 1 includes a main body case 2, a rotating shaft 3, a cylinder block 4, a piston 5, a shoe 6, a swash plate 7, a tilting piston 8, and the like.
(本体ケースおよび回転軸)
本体ケース2は、回転軸3、シリンダブロック4、ピストン5、斜板7などを収納するためのものであり、回転軸3は、本体ケース2に対して回転自在に保持されている。 (Main unit case and rotating shaft)
Themain body case 2 is for housing the rotary shaft 3, the cylinder block 4, the piston 5, the swash plate 7 and the like, and the rotary shaft 3 is held rotatably with respect to the main body case 2.
本体ケース2は、回転軸3、シリンダブロック4、ピストン5、斜板7などを収納するためのものであり、回転軸3は、本体ケース2に対して回転自在に保持されている。 (Main unit case and rotating shaft)
The
(シリンダブロック)
シリンダブロック4は、回転軸3に対してスプライン結合され、回転軸3の軸方向Xには移動可能に、回転軸3の回転方向には回転軸3とともに回転するように回転軸3に取り付けられている。また、シリンダブロック4の軸心まわりには軸方向に穿設された複数のシリンダ穴4aが形成されている。これらのシリンダ穴4aは、同一円周上に等間隔で配置されている。シリンダ穴4aは、その長手方向が軸方向Xと平行になるようにシリンダブロック4に形成されている。 (Cylinder block)
Thecylinder block 4 is spline-coupled to the rotating shaft 3 and is attached to the rotating shaft 3 so as to be movable in the axial direction X of the rotating shaft 3 and to rotate together with the rotating shaft 3 in the rotating direction of the rotating shaft 3. ing. A plurality of cylinder holes 4 a are formed in the axial direction around the axis of the cylinder block 4. These cylinder holes 4a are arranged at equal intervals on the same circumference. The cylinder hole 4 a is formed in the cylinder block 4 so that its longitudinal direction is parallel to the axial direction X.
シリンダブロック4は、回転軸3に対してスプライン結合され、回転軸3の軸方向Xには移動可能に、回転軸3の回転方向には回転軸3とともに回転するように回転軸3に取り付けられている。また、シリンダブロック4の軸心まわりには軸方向に穿設された複数のシリンダ穴4aが形成されている。これらのシリンダ穴4aは、同一円周上に等間隔で配置されている。シリンダ穴4aは、その長手方向が軸方向Xと平行になるようにシリンダブロック4に形成されている。 (Cylinder block)
The
(ピストンおよびシュー)
ピストン5は、複数備えられており、シリンダ穴4aの各々にシリンダ穴4aの内壁面に対して摺動自在に挿入されている。ピストン5の先端に形成された球体部にはシュー6が取り付けられている。 (Piston and shoe)
Plural pistons 5 are provided, and are inserted into the cylinder holes 4a so as to be slidable with respect to the inner wall surface of the cylinder hole 4a. A shoe 6 is attached to a sphere formed at the tip of the piston 5.
ピストン5は、複数備えられており、シリンダ穴4aの各々にシリンダ穴4aの内壁面に対して摺動自在に挿入されている。ピストン5の先端に形成された球体部にはシュー6が取り付けられている。 (Piston and shoe)
(斜板)
斜板7は、シュー6が摺動する斜面7aと、斜面7aの反対側に形成され本体ケース2に対して支持される支持面7bと、を有する。斜板7は、軸方向Xからみて環状に形成されており、回転軸3が貫通している。 (Swash plate)
Theswash plate 7 has an inclined surface 7 a on which the shoe 6 slides, and a support surface 7 b that is formed on the opposite side of the inclined surface 7 a and is supported with respect to the main body case 2. The swash plate 7 is formed in an annular shape when viewed from the axial direction X, and the rotating shaft 3 passes therethrough.
斜板7は、シュー6が摺動する斜面7aと、斜面7aの反対側に形成され本体ケース2に対して支持される支持面7bと、を有する。斜板7は、軸方向Xからみて環状に形成されており、回転軸3が貫通している。 (Swash plate)
The
シリンダブロック4の各シリンダ穴4aに圧油が給排されると、各々のシリンダ穴4aに挿入されているピストン5が往復動する。このピストン5の往復動にともなってシュー6が斜板7の斜面7a上を摺動しながら回転し当該ピストン5も回転する。そして、ピストン5の回転によりシリンダブロック4が回転し、シリンダブロック4と一体となって回転軸3が回転するようになっている。
When the pressure oil is supplied to and discharged from each cylinder hole 4a of the cylinder block 4, the piston 5 inserted into each cylinder hole 4a reciprocates. As the piston 5 reciprocates, the shoe 6 rotates while sliding on the inclined surface 7a of the swash plate 7, and the piston 5 also rotates. The cylinder block 4 is rotated by the rotation of the piston 5, and the rotating shaft 3 is rotated integrally with the cylinder block 4.
斜板7の支持面7bは、回転軸3の軸方向Xに対する角度の異なる2つの面である第1支持面7b1と第2支持面7b2とで構成されている。第1支持面7b1と第2支持面7b2とが交差する交差線上であって回転軸3の両側にはピボット11が斜板7の支持面7bに対して摺動自在に配置されている。これら2個のピボット11は本体ケース2に固定されている。斜板7は、第1支持面7b1が本体ケース2に当接する位置(図3参照)と第2支持面7b2が本体ケース2に当接する位置(図1参照)との間で2個のピボット11を支点として揺動するようになっている。
The support surface 7b of the swash plate 7 includes a first support surface 7b1 and a second support surface 7b2 which are two surfaces having different angles with respect to the axial direction X of the rotary shaft 3. Pivots 11 are slidably disposed on the support surface 7b of the swash plate 7 on both sides of the rotary shaft 3 on the intersecting line where the first support surface 7b1 and the second support surface 7b2 intersect. These two pivots 11 are fixed to the main body case 2. The swash plate 7 has two pivots between a position where the first support surface 7b1 contacts the main body case 2 (see FIG. 3) and a position where the second support surface 7b2 contacts the main body case 2 (see FIG. 1). 11 is used as a fulcrum.
(傾転ピストン)
斜板7の第2支持面7b2が本体ケース2に当接する部分の本体ケース2内壁面には、傾転ピストン8が摺動自在に挿入される断面円形の傾転ピストン用シリンダ穴9が設けられている。この傾転ピストン用シリンダ穴9に、斜板7をピストン5側に向かって押圧することで当該斜板7を傾転させる(揺動させる)傾転ピストン8が挿入されている。 (Tilt piston)
On the inner wall surface of themain body case 2 where the second support surface 7b2 of the swash plate 7 comes into contact with the main body case 2, there is provided a tilt piston cylinder hole 9 having a circular cross section into which the tilt piston 8 is slidably inserted. It has been. A tilting piston 8 that tilts (swings) the swash plate 7 by inserting the swash plate 7 toward the piston 5 is inserted into the tilting piston cylinder hole 9.
斜板7の第2支持面7b2が本体ケース2に当接する部分の本体ケース2内壁面には、傾転ピストン8が摺動自在に挿入される断面円形の傾転ピストン用シリンダ穴9が設けられている。この傾転ピストン用シリンダ穴9に、斜板7をピストン5側に向かって押圧することで当該斜板7を傾転させる(揺動させる)傾転ピストン8が挿入されている。 (Tilt piston)
On the inner wall surface of the
図2に示したように、傾転ピストン8は、円筒状であって傾転ピストン用シリンダ穴9の内壁面と摺動する本体部8aと、斜板7側の本体部8a端面に当該本体部8aと一体的に形成された球面部8bとを有する。なお、一体的に形成されたとは、本体部8aと球面部8bとを有する傾転ピストン8が一つの素材から鋳造、削り出しなどにより製作されていることをいう。本体部8aと球面部8bとがそれぞれ別に製作された部品ではないことをいう。
As shown in FIG. 2, the tilting piston 8 has a cylindrical body 8a that slides on the inner wall surface of the tilting piston cylinder hole 9, and the main body 8a on the end face of the main body 8a on the swash plate 7 side. And a spherical portion 8b formed integrally with the portion 8a. The term “integrally formed” means that the tilting piston 8 having the main body portion 8a and the spherical surface portion 8b is manufactured from one material by casting, cutting, or the like. This means that the main body portion 8a and the spherical surface portion 8b are not separately manufactured parts.
球面部8bとは反対側の本体部8aの端と傾転ピストン用シリンダ穴9の底面との間には、傾転ピストン8作動用の圧油が導入される背圧室13が形成されている。なお、傾転ピストン8を作動させるための背圧室13への圧油は、本体ケース2に設けられた油路14を介して供給されるようになっている。また、傾転ピストン8は、背圧室13に配置されたコイルばね12により、常時、斜板7側に付勢されている。傾転ピストン8は、切換弁(不図示)が切り換えられて油路14を介して圧油が背圧室13に供給されることで斜板7をピストン5側に向かって押圧するようになっている。これにより、斜板7の傾転角度が変わって高速から低速へ油圧モータ1は切り換わる(図1参照)。背圧室13への圧油の供給をやめると、背圧室13から油が抜けて傾転ピストン8が後退し、斜板7の傾転角度が変わって低速から高速へ油圧モータ1は切り換わる(図3参照)。
A back pressure chamber 13 into which pressure oil for operating the tilting piston 8 is introduced is formed between the end of the main body 8a opposite to the spherical surface 8b and the bottom surface of the tilting piston cylinder hole 9. Yes. In addition, the pressure oil to the back pressure chamber 13 for operating the tilting piston 8 is supplied through an oil passage 14 provided in the main body case 2. The tilting piston 8 is always urged toward the swash plate 7 by a coil spring 12 disposed in the back pressure chamber 13. The tilting piston 8 presses the swash plate 7 toward the piston 5 side by switching a switching valve (not shown) and supplying pressure oil to the back pressure chamber 13 through the oil passage 14. ing. As a result, the tilt angle of the swash plate 7 changes and the hydraulic motor 1 switches from high speed to low speed (see FIG. 1). When the supply of pressure oil to the back pressure chamber 13 is stopped, the oil escapes from the back pressure chamber 13 and the tilting piston 8 moves backward, and the tilting angle of the swash plate 7 changes to switch the hydraulic motor 1 from low to high. (See FIG. 3).
(プレート部材)
斜板7と傾転ピストン8との間にはプレート部材10が配置されている。プレート部材10は、傾転ピストン8の球面部8bが摺動自在に嵌り込む当該球面部8bと同形状の凹部10aと、斜板7の第2支持面7b2に形成された第2支持面7b2の一部である円形の凹部7cと摺動する平らな摺動面10bと、を有する円板状の部材である。摺動面10bの外周縁部は面取り10cが施されている。傾転ピストン8の球面部8bとプレート部材10の凹部10a、およびプレート部材10の摺動面10bと斜板7の凹部7cとは、いずれも面接触するように形成されている。 (Plate member)
Aplate member 10 is disposed between the swash plate 7 and the tilting piston 8. The plate member 10 includes a concave portion 10a having the same shape as the spherical portion 8b into which the spherical portion 8b of the tilting piston 8 is slidably fitted, and a second support surface 7b2 formed on the second support surface 7b2 of the swash plate 7. It is a disk-shaped member which has the circular recessed part 7c which is a part, and the flat sliding surface 10b which slides. The outer peripheral edge of the sliding surface 10b is chamfered 10c. The spherical surface portion 8b of the tilting piston 8 and the concave portion 10a of the plate member 10, and the sliding surface 10b of the plate member 10 and the concave portion 7c of the swash plate 7 are all formed in surface contact.
斜板7と傾転ピストン8との間にはプレート部材10が配置されている。プレート部材10は、傾転ピストン8の球面部8bが摺動自在に嵌り込む当該球面部8bと同形状の凹部10aと、斜板7の第2支持面7b2に形成された第2支持面7b2の一部である円形の凹部7cと摺動する平らな摺動面10bと、を有する円板状の部材である。摺動面10bの外周縁部は面取り10cが施されている。傾転ピストン8の球面部8bとプレート部材10の凹部10a、およびプレート部材10の摺動面10bと斜板7の凹部7cとは、いずれも面接触するように形成されている。 (Plate member)
A
ここで、本実施形態では、プレート部材10の直径D1は傾転ピストン用シリンダ穴9の直径D2よりも小さくされている。また、図1に示すように、斜板7が低速位置にあるときに、傾転ピストン用シリンダ穴9の開口側端面よりも斜板7側にプレート部材10が配置されている。第2支持面7b2の一部である円形の凹部7cの深さは、プレート部材10の厚みと等しい。すなわち、斜板7の第2支持面7b2(凹部7cではない位置)とプレート部材10とは面一とされている。また、第2支持面7b2の凹部7cの内径は、プレート部材10の直径D1よりも大きくされている。すなわち、プレート部材10と凹部7cとの間には隙間があり、プレート部材10は、凹部7cの底面と当接しつつ凹部7c内を移動可能とされている。
Here, in this embodiment, the diameter D1 of the plate member 10 is smaller than the diameter D2 of the cylinder hole 9 for the tilting piston. Further, as shown in FIG. 1, when the swash plate 7 is at the low speed position, the plate member 10 is disposed on the swash plate 7 side of the opening side end surface of the tilting piston cylinder hole 9. The depth of the circular recess 7c that is a part of the second support surface 7b2 is equal to the thickness of the plate member 10. That is, the second support surface 7b2 (a position that is not the recess 7c) of the swash plate 7 and the plate member 10 are flush with each other. Further, the inner diameter of the concave portion 7 c of the second support surface 7 b 2 is made larger than the diameter D 1 of the plate member 10. That is, there is a gap between the plate member 10 and the recess 7c, and the plate member 10 is movable in the recess 7c while being in contact with the bottom surface of the recess 7c.
(作用・効果)
本実施形態の油圧モータ1では、斜板7と傾転ピストン8とがプレート部材10を介して当接する。ここで、傾転ピストン8とプレート部材10との接触面積、およびプレート部材10と斜板7との接触面積は、いずれも、特許文献1(特開2004-169654号公報)に記載されたような従来の斜板と傾転ピストンとの接触面積に比べて増加する。したがって、傾転ピストン8の押圧力は従来のような集中荷重とはならない。すなわち、本実施形態によると、製作容易なプレート部材10を斜板7と傾転ピストン8との間に挟み込むだけで、熱処理などの硬化処理を斜板7に施すことなく、斜板7の摩耗・割れを防止することができる。また、プレート部材10が、斜板7の凹部7cの底面と当接しつつ凹部7c内を移動可能とされているため、接触している傾転ピストン8の球面部8bとプレート部材10の凹部10aとの間の相対的なズレが生じにくくなっている。そのため、球面部8bおよび凹部10aの摩耗が生じにくい。 (Action / Effect)
In thehydraulic motor 1 of the present embodiment, the swash plate 7 and the tilting piston 8 abut via the plate member 10. Here, the contact area between the tilting piston 8 and the plate member 10 and the contact area between the plate member 10 and the swash plate 7 are all described in Patent Document 1 (Japanese Patent Laid-Open No. 2004-169654). The contact area between the conventional swash plate and the tilting piston increases. Therefore, the pressing force of the tilting piston 8 does not become a concentrated load as in the prior art. That is, according to the present embodiment, the plate member 10 that is easy to manufacture is simply sandwiched between the swash plate 7 and the tilting piston 8, and the swash plate 7 is worn without being subjected to a hardening process such as heat treatment. -It can prevent cracking. Further, since the plate member 10 is movable in the recess 7c while being in contact with the bottom surface of the recess 7c of the swash plate 7, the spherical portion 8b of the tilting piston 8 and the recess 10a of the plate member 10 that are in contact with each other. The relative deviation between the two is less likely to occur. Therefore, wear of the spherical surface portion 8b and the concave portion 10a is unlikely to occur.
本実施形態の油圧モータ1では、斜板7と傾転ピストン8とがプレート部材10を介して当接する。ここで、傾転ピストン8とプレート部材10との接触面積、およびプレート部材10と斜板7との接触面積は、いずれも、特許文献1(特開2004-169654号公報)に記載されたような従来の斜板と傾転ピストンとの接触面積に比べて増加する。したがって、傾転ピストン8の押圧力は従来のような集中荷重とはならない。すなわち、本実施形態によると、製作容易なプレート部材10を斜板7と傾転ピストン8との間に挟み込むだけで、熱処理などの硬化処理を斜板7に施すことなく、斜板7の摩耗・割れを防止することができる。また、プレート部材10が、斜板7の凹部7cの底面と当接しつつ凹部7c内を移動可能とされているため、接触している傾転ピストン8の球面部8bとプレート部材10の凹部10aとの間の相対的なズレが生じにくくなっている。そのため、球面部8bおよび凹部10aの摩耗が生じにくい。 (Action / Effect)
In the
また、本実施形態では、斜板7とプレート部材10とが軸方向Xでラップするので、斜板7と傾転ピストン8との間にプレート部材10を配置したとしても、傾転ピストン8の軸方向長さを従来よりも短くする必要がない。すなわち、傾転ピストン8の軸方向長さを従来と同様の長さとすることができ、傾転ピストン8が傾くことに起因する傾転ピストン用シリンダ穴9の偏摩耗を防止できる。なお、別の観点では、油圧モータ1の軸方向長さを従来よりも長くする必要がない、という効果もある。
In this embodiment, since the swash plate 7 and the plate member 10 wrap in the axial direction X, even if the plate member 10 is disposed between the swash plate 7 and the tilt piston 8, the tilt piston 8 It is not necessary to make the axial length shorter than before. That is, the axial length of the tilting piston 8 can be made the same as that of the conventional one, and uneven wear of the tilting piston cylinder hole 9 due to the tilting of the tilting piston 8 can be prevented. In addition, from another viewpoint, there is an effect that the axial length of the hydraulic motor 1 does not need to be longer than that in the related art.
(プレート部材の径)
ここで、本実施形態では、プレート部材10の直径D1を傾転ピストン用シリンダ穴9の直径D2よりも小さくしているが、プレート部材10の直径D1を傾転ピストン用シリンダ穴9の直径D2よりも大きくすることも好ましい。すなわち、プレート部材10の摺動面10bの面積を、傾転ピストン用シリンダ穴9の面積よりも大きくすることも好ましい。このようにすることで、プレート部材10の受圧面積が大きくなり面圧が下がるので、安価な金属素材を用いてプレート部材10を製作することが可能となる。なお、プレート部材10は円板状でなくてもよく、例えば、楕円板状などであってもよい。 (Diameter of plate member)
In this embodiment, the diameter D1 of theplate member 10 is smaller than the diameter D2 of the tilting piston cylinder hole 9, but the diameter D1 of the plate member 10 is set to the diameter D2 of the tilting piston cylinder hole 9. It is also preferable to make it larger. That is, it is also preferable that the area of the sliding surface 10 b of the plate member 10 is larger than the area of the tilting piston cylinder hole 9. By doing in this way, since the pressure receiving area of the plate member 10 becomes large and a surface pressure falls, it becomes possible to manufacture the plate member 10 using an inexpensive metal raw material. In addition, the plate member 10 may not be disk shape, for example, elliptical plate shape etc. may be sufficient.
ここで、本実施形態では、プレート部材10の直径D1を傾転ピストン用シリンダ穴9の直径D2よりも小さくしているが、プレート部材10の直径D1を傾転ピストン用シリンダ穴9の直径D2よりも大きくすることも好ましい。すなわち、プレート部材10の摺動面10bの面積を、傾転ピストン用シリンダ穴9の面積よりも大きくすることも好ましい。このようにすることで、プレート部材10の受圧面積が大きくなり面圧が下がるので、安価な金属素材を用いてプレート部材10を製作することが可能となる。なお、プレート部材10は円板状でなくてもよく、例えば、楕円板状などであってもよい。 (Diameter of plate member)
In this embodiment, the diameter D1 of the
以上、本発明の実施形態について説明したが、本発明は上述の実施の形態に限られるものではなく、特許請求の範囲に記載した限りにおいて様々に変更して実施することができるものである。
As mentioned above, although embodiment of this invention was described, this invention is not limited to the above-mentioned embodiment, As long as it described in the claim, it can implement variously.
1:油圧モータ(斜板式油圧モータ)
2:本体ケース
3:回転軸
4:シリンダブロック
5:ピストン
6:シュー
7:斜板
8:傾転ピストン
8b:球面部
9:傾転ピストン用シリンダ穴
10:プレート部材 1: Hydraulic motor (swash plate type hydraulic motor)
2: Body case 3: Rotating shaft 4: Cylinder block 5: Piston 6: Shoe 7: Swash plate 8:Tilt piston 8b: Spherical surface portion 9: Tilt piston cylinder hole 10: Plate member
2:本体ケース
3:回転軸
4:シリンダブロック
5:ピストン
6:シュー
7:斜板
8:傾転ピストン
8b:球面部
9:傾転ピストン用シリンダ穴
10:プレート部材 1: Hydraulic motor (swash plate type hydraulic motor)
2: Body case 3: Rotating shaft 4: Cylinder block 5: Piston 6: Shoe 7: Swash plate 8:
Claims (3)
- 本体ケースと、
前記本体ケース内に収納された回転軸と、
前記回転軸に取り付けられたシリンダブロックと、
前記シリンダブロックに形成された複数のシリンダ穴と、
前記シリンダ穴に摺動自在に挿入されたピストンと、
前記ピストンの先端に設けられたシューと、
前記シューが摺動する斜面と、当該斜面の反対側に形成され前記本体ケースに対して支持される支持面と、を有する斜板と、
前記斜板の支持面に当接し、当該斜板を前記ピストン側に向かって押圧することで当該斜板を傾転させる傾転ピストンと、
前記本体ケースに形成され前記傾転ピストンが摺動自在に挿入される傾転ピストン用シリンダ穴と、
を備える斜板式油圧モータ又は斜板式油圧ポンプにおいて、
前記傾転ピストンの斜板側端面に球面部が一体的に形成されており、
傾転ピストン側に前記球面部が摺動自在に嵌り込む当該球面部と同形状の凹部と、斜板側に前記支持面と摺動する摺動面と、を有するプレート部材が、前記斜板と前記傾転ピストンとの間に配置されていることを特徴とする斜板式油圧モータ又は斜板式油圧ポンプ。 A body case,
A rotating shaft housed in the body case;
A cylinder block attached to the rotating shaft;
A plurality of cylinder holes formed in the cylinder block;
A piston slidably inserted into the cylinder hole;
A shoe provided at the tip of the piston;
A swash plate having a slope on which the shoe slides, and a support surface formed on the opposite side of the slope and supported by the body case;
A tilting piston that abuts the support surface of the swash plate and tilts the swash plate by pressing the swash plate toward the piston;
A cylinder hole for a tilting piston that is formed in the main body case and into which the tilting piston is slidably inserted;
In a swash plate type hydraulic motor or swash plate type hydraulic pump comprising:
A spherical portion is integrally formed on the end surface of the tilting piston on the swash plate side,
A plate member having a concave portion having the same shape as the spherical surface portion into which the spherical surface portion is slidably fitted on the tilting piston side, and a sliding surface sliding on the support surface on the swash plate side, A swash plate type hydraulic motor or a swash plate type hydraulic pump, wherein the swash plate type hydraulic motor or swash plate type hydraulic pump is disposed between the swash plate type piston and the tilting piston. - 請求項1に記載の斜板式油圧モータ又は斜板式油圧ポンプにおいて、
前記斜板が低速位置にあるときに、前記傾転ピストン用シリンダ穴の開口側端面よりも斜板側に前記プレート部材が配置されていることを特徴とする斜板式油圧モータ又は斜板式油圧ポンプ。 In the swash plate type hydraulic motor or swash plate type hydraulic pump according to claim 1,
The swash plate type hydraulic motor or swash plate type hydraulic pump, wherein the plate member is disposed closer to the swash plate side than the opening side end face of the tilting piston cylinder hole when the swash plate is at a low speed position. . - 請求項2に記載の斜板式油圧モータ又は斜板式油圧ポンプにおいて、
前記プレート部材の摺動面の面積が、前記傾転ピストン用シリンダ穴の面積よりも大きくされていることを特徴とする斜板式油圧モータ又は斜板式油圧ポンプ。 In the swash plate type hydraulic motor or swash plate type hydraulic pump according to claim 2,
A swash plate type hydraulic motor or a swash plate type hydraulic pump, wherein an area of a sliding surface of the plate member is larger than an area of the cylinder hole for the tilting piston.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2011148092A JP5756691B2 (en) | 2011-07-04 | 2011-07-04 | Swash plate type hydraulic motor or swash plate type hydraulic pump |
JP2011-148092 | 2011-07-04 |
Publications (1)
Publication Number | Publication Date |
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WO2013005703A1 true WO2013005703A1 (en) | 2013-01-10 |
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PCT/JP2012/066841 WO2013005703A1 (en) | 2011-07-04 | 2012-07-02 | Swash plate type hydraulic motor and swash plate type hydraulic pump |
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WO (1) | WO2013005703A1 (en) |
Cited By (1)
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WO2020152909A1 (en) * | 2019-01-24 | 2020-07-30 | Kyb株式会社 | Hydraulic rotary machine |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
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JP6220260B2 (en) * | 2013-12-19 | 2017-10-25 | 株式会社豊田自動織機 | Variable displacement piston pump |
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JPH0512667U (en) * | 1991-07-29 | 1993-02-19 | カヤバ工業株式会社 | Variable hydraulic motor |
JPH0573270U (en) * | 1991-04-19 | 1993-10-08 | 住友建機株式会社 | 2nd speed switching structure of swash plate hydraulic motor |
JPH0754758A (en) * | 1993-08-11 | 1995-02-28 | Kubota Corp | Swash plate angle adjusting structure for variable displacement oil hydraulic motor |
JP2005105899A (en) * | 2003-09-29 | 2005-04-21 | Kayaba Ind Co Ltd | Swash plate type hydraulic pump motor |
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2011
- 2011-07-04 JP JP2011148092A patent/JP5756691B2/en active Active
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JPH0573270U (en) * | 1991-04-19 | 1993-10-08 | 住友建機株式会社 | 2nd speed switching structure of swash plate hydraulic motor |
JPH0512667U (en) * | 1991-07-29 | 1993-02-19 | カヤバ工業株式会社 | Variable hydraulic motor |
JPH0754758A (en) * | 1993-08-11 | 1995-02-28 | Kubota Corp | Swash plate angle adjusting structure for variable displacement oil hydraulic motor |
JP2005105899A (en) * | 2003-09-29 | 2005-04-21 | Kayaba Ind Co Ltd | Swash plate type hydraulic pump motor |
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Publication number | Priority date | Publication date | Assignee | Title |
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WO2020152909A1 (en) * | 2019-01-24 | 2020-07-30 | Kyb株式会社 | Hydraulic rotary machine |
JP2020118097A (en) * | 2019-01-24 | 2020-08-06 | Kyb株式会社 | Hydraulic rotary machine |
JP7128753B2 (en) | 2019-01-24 | 2022-08-31 | Kyb株式会社 | hydraulic rotary machine |
US11549497B2 (en) | 2019-01-24 | 2023-01-10 | Kyb Corporation | Hydraulic rotating machine |
Also Published As
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JP2013015066A (en) | 2013-01-24 |
JP5756691B2 (en) | 2015-07-29 |
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