CN105443338A - Tandem hydraulic pump - Google Patents
Tandem hydraulic pump Download PDFInfo
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- CN105443338A CN105443338A CN201510591462.XA CN201510591462A CN105443338A CN 105443338 A CN105443338 A CN 105443338A CN 201510591462 A CN201510591462 A CN 201510591462A CN 105443338 A CN105443338 A CN 105443338A
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Abstract
The invention provides a tandem hydraulic pump with ejection flow paths of two systems. The ejection flow paths of each system is characterized in that two ends in the flow in direction of pressure oil are provided with at least two flow in ports which faces an axis direction and is used for flowing in pressure oil ejected from the ejection port of each pump unit, and a flow out port which faces the direction orthogonal with the axis direction and is used for flowing out the pressure oil. The ejection flow paths of each system is provided with a converging unit midway in the flow direction of pressure oil; the converging unit converges pressure oil flowing from at least two flow in ports and guides the pressure oil into a flow out port; when the ejection flow paths of the two system are axially observed, overlapping regions are partially spaced so as to allow the shortest size among the inner walls of the ejection flow paths of the two system is configured according to a preset interval mode; the side of the converging unit configured closerer to the flow out port than the overlapping regions, and part of the side of the ejection flow paths closerer to the flow in ports than the converging unit form two paths respectively communicated with the two flow in ports.
Description
Technical field
Embodiments of the present invention relate to a kind of serial type oil hydraulic pump.
Background technique
Such as the hydraulic power that the engineering machinery such as hydraulic shovel use, be known to a kind of serial type oil hydraulic pump possessing two pump unit.In this serial type oil hydraulic pump, configuring two pump unit with arranging vertically, by making the coaxial running shaft synchronous rotary combined, making two pump cell operation.
In this serial type oil hydraulic pump, the housing of accommodation two pump unit is formed with suction passage and ejection path.Suction passage is the stream for each suction port supply working oil to two pump unit.In addition, spraying stream is that pressure oil for being gushed out by the ejiction opening from two pump unit exports to outside stream.In general, spray stream and be provided with two systems independently of each other to the pressure oil gushed out from two pump unit is supplied to different streams.
These suction passages and ejection stream normally collect and are configured on middle casing (the intermediate portion region of housing), and this middle casing is located at the intermediate portion of two the pump unit be axially provided separately.Middle casing is connected to each pump unit by valve block.
At this, the ejection stream of two systems is configured in and is separated from each other vertically but close position.
In addition, in the part of ejection stream being formed with two systems, consider security intensity and need to guarantee in advance to be enough to stand the wall thickness using pressure between ejection stream.Further, it is expected that the outlet (outflow opening) being designed to the ejection stream from the ejiction opening of each pump unit to middle casing makes the pressure loss little as much as possible.
Therefore, there is the situation such as forming two mouths at the position corresponding with the ejiction opening of each pump unit of valve block respectively.In this case, middle casing is formed the stream by the face of valve block side is collaborated making two mouths at middle casing.And result corresponds to each pump unit and forms ejection stream (the ejection streams of two systems) on middle casing.
In addition, in order to seek to reduce the pressure loss in middle casing, expect in advance the flow path cross sectional area of the ejection stream of middle casing to be expanded as much as possible.Therefore, due to guarantee the ejection stream of two systems the part from overlap during end on observation (below this part being called " overlap region part ") needed for size, therefore the axial dimension of middle casing becomes large.Its result, the total length in the axis (input shaft direction) of serial type oil hydraulic pump can be elongated, likely fully cannot meet the requirement of the shortening pump total length of adjoint engineering machinery compactness in recent years.
Prior art document
Te Xu document
Te Xu document 1: Japanese Unexamined Patent Publication 2001-140749 publication
Summary of the invention
the problem that invention will solve
The present invention is to provide a kind of and can seeks to shorten the axial dimension in the intermediate portion region of the housing that the ejection stream for two systems is formed for the problem solved, can shorten the serial type oil hydraulic pump of entire axial length thus.
for the scheme of dealing with problems
The serial type oil hydraulic pump of mode of execution has the ejection stream of housing, two pump unit, suction passage, two systems.Two pump unit are arranged in housing in the axial direction dividually.Suction passage is located on housing, and each suction port respectively to two pump unit imports working oil.The ejection stream of two systems is located on housing, respectively the pressure oil of each ejiction opening ejection from two pump unit is exported to outside for each pump unit.And be located in the intermediate portion region of the intermediate portion of two the pump unit axially arranged dividually at housing, the ejection stream of two systems configures in the axial direction apart from each other.In addition, the ejection stream of each system has at least two inflow entrances, outflow opening, a merging part.Inflow entrance, towards axis, flows into for the pressure oil sprayed from the ejiction opening of each pump unit respectively.Outflow opening, towards direction orthogonal to the axial direction, flows out to outside for making pressure oil.These inflow entrances and ejiction opening are configured in the two ends on the flow direction of pressure oil respectively.Merging part makes the midway of pressure oil on the flow direction of pressure oil flowed into from least two inflow entrances collaborate and the outflow opening that leads.And, the overlap region part from overlap during end on observation of the ejection stream of two systems open with sky that to make between the inwall of the ejection stream of two systems the shortest and be of a size of predetermined more than the mode at such interval configure.In addition, merging part is configured in than the side of overlapping area part near outflow opening.And what spray stream is positioned at two streams being configured to be communicated in respectively two inflow entrances than the part of merging part near the side of inflow entrance.
Accompanying drawing explanation
Fig. 1 is the longitudinal section of the serial type oil hydraulic pump representing the 1st mode of execution.
Fig. 2 is the structural drawing of the middle casing of the serial type oil hydraulic pump representing the 1st mode of execution, and (A) is side view, and (B) is axial end view drawing.
Fig. 3 is the structural drawing of the middle casing of the serial type oil hydraulic pump representing the 2nd mode of execution, and (A) is side view, and (B) is axial end view drawing.
description of reference numerals
1, serial type oil hydraulic pump; 10, housing; 11A, 11B, shell main body; 13, middle casing (the intermediate portion region of housing); 13A, 13B, end face axially; 13C, outer side surface; 30A, 30B, pump unit; 34A, 34B, valve block; 51A, 51B, suction port; 53A, 53B, suction passage; 60A, 60B, ejection stream; 61A, 61B, ejiction opening; 62A, 62B, inflow entrance; 63A, 63B, outflow opening; 66A, 66B, merging part; The shortest size between SA, inwall; 64A, 65A, two streams; 64B, 65B, two streams; 113, middle casing (the intermediate portion region of housing); 160A, 160B, ejection stream; 162A, 162B, inflow entrance; 163A, 163B, outflow opening; 166A, 166B, stream; R1, R2, overlap region part; Sectional dimension on T1, the direction mutually orthogonal with axis; T2, sectional dimension axially.
Embodiment
Hereinafter, with reference to the accompanying drawings of the serial type oil hydraulic pump of mode of execution.
(the 1st mode of execution)
Fig. 1 is the longitudinal section of the serial type oil hydraulic pump representing the 1st mode of execution.
This serial type oil hydraulic pump 1 (below sometimes referred to as " oil hydraulic pump 1 ") is such as the serial type cam-type axial piston pump be mounted in as hydraulic power in the engineering machinery such as hydraulic shovel.
This oil hydraulic pump 1 have formed housing integration housing 10 and to rotate the input shaft (running shaft) 20 that mode is freely configured in the central part of housing 10.Input shaft 20 can be driven by rotary driving sources such as the motors be arranged on outside pump and rotate.In housing 10, the axis (left and right directions of Fig. 1) of input shaft 20 accommodates two pump unit 30A, 30B dividually.Below, the right-hand member side in Fig. 1 is called forward end, left end side is called rear end side, the pump unit 30A of forward end is called the 1st pump unit, the pump unit 30B of rear end side is called the 2nd pump unit and is described.
Housing 10 comprises the 1st shell main body 11A of forward end, the 2nd shell main body 11B of rear end side, the front shroud 12A of the front opening of inaccessible 1st shell main body 11A, the back cover 12B of the open rearward end of inaccessible 2nd shell main body 11B and the middle casing 13 that is clipped between the 1st shell main body 11A and the 2nd shell main body 11B.These components arrange from the forward end of axis towards rear end side according to the order of front shroud 12A, the 1st shell main body 11A, middle casing 13, the 2nd shell main body 11B, back cover 12B.Middle casing 13 forms the intermediate portion region axially of housing 10.And the 1st pump unit 30A is contained in the 1st shell main body 11A of the tubular being configured at forward end, the 2nd pump unit 30B is contained in the 2nd shell main body 11B of the tubular being configured at rear end side.
At this, being formed by the 1st shell main body 11A indicating reference character " A " with the part of middle casing 13 forward end that is border of housing 10, being formed by the 2nd shell main body 11B indicating reference character " B " with the part of middle casing 13 rear end side that is border of housing 10.Therefore, for housing 10 and pump unit 30A, 30B, to being located at the element numeral reference character " A " of forward end, being located at the element numeral reference character " B " of rear end side in forward end and the paired component of rear end side.
Two pump unit 30A, 30B are configured to the cam-type axial piston pump that can adjust the variable capacity type of ejection capacity respectively.Each pump unit 30A, 30B of being configured to cam-type axial piston pump comprise swash plate 35A, the 35B, multiple plunger 33A, 33B, cylinder body 31A, 31B, valve block (valve plate) 34A, 34B, running shaft 21,22 etc. of annulus tabular respectively.Described each component respectively with middle casing 13 for benchmark and in the axial direction line configure symmetrically.That is, valve block 34A, 34B is configured in the position contacted with both ends of the surface 13A axially, the 13B of middle casing 13 respectively.
Swash plate 35A is configured in the inside of shell main body 11A, by swash plate support member 36A with the internal surface that the mode of deflection angle can be regulated to be arranged on front shroud 12A, swash plate 35B is configured in the inside of shell main body 11B, by swash plate support member 36B with the internal surface that the mode of deflection angle can be regulated to be arranged on back cover 12B.Be provided with near swash plate support member 36A, 36B by swash plate support member 36A, 36B to adjust the deflection angle adjustment component such as the deflection plunger of the deflection angle of swash plate 35A, 35B (omitting diagram).
The deflection angle adjustment component such as deflection plunger mainly do not illustrate in FIG in view of the relation be configured in the longitudinal section orthogonal with Fig. 1, and it utilizes the pressure of hydraulic control pump 80 carry out work and control the deflection angle of swash plate 35A, 35B.Swash plate 35A, 35B can comprise input shaft 20 central axis L, freely adjust deflection angle in orthogonal with Fig. 1 longitudinal section.As aftermentioned, when the deflection angle change of swash plate 35A, 35B, the path increment of each plunger 33A, 33B changes, thus controls the flow of the pressure oil of self-pumping unit 30A, 30B ejection.
Swash plate 35A, 35B have even surface in the side contrary with swash plate support member 36A, 36B, and piston shoes 39A, 39B along the circumferential direction slidably contact with this even surface.Each plunger 33A, 33B engage with piston shoes 39A, 39B in the mode that can swing by the ball head on its top.
Piston shoes 39A, 39B by retaining plate 37B can be supported by snap features 38A, the 38B be arranged on input shaft 20 periphery with the mode of swash plate 35A, 35B together deflection.
Cylinder body 31A, 31B are formed as cylindric, are contained in shell main body 11A, 11B in the mode that can rotate.Multiple cylinder body room (also referred to as cylinder barrel) 32A, 32B of plunger 33A, 33B being kept in the mode that can slide are formed in cylinder body 31A, 31B.32A, 32B are equally spaced formed in a circumferential direction around the spin axis (consistent with the central axis L of input shaft 20) of cylinder body 31A, 31B for multiple cylinder body room.
The center hole of the cylinder body 31A of the through 1st pump unit 30A of state that the 1st running shaft 21 is fitted together to spline.In addition, the center hole of the cylinder body 31B of the through 2nd pump unit 30B of state that is fitted together to spline of the 2nd running shaft 22.1st running shaft 21 is supported to rotate mode freely with the needle bearing 27A being arranged on the rear side on middle casing 13 by the tapered roller bearing 26A of the front side be arranged on front shroud 12A.In addition, the 2nd running shaft 22 is supported to rotate mode freely with the needle bearing 27B being arranged on the front side on middle casing 13 by the tapered roller bearing 26B of the rear side be arranged on back cover 12B.
1st running shaft 21 and the 2nd running shaft 22 configure front side on the same axis and rear side respectively, and they are connected to each other by coupling 25 chimeric with the rear end of the 1st running shaft 21 and the front end spline of the 2nd running shaft 22 respectively, to realize synchronous rotary.And, described utilize coupling 25 to link up the 1st running shaft 21 and the 2nd running shaft 22 form an input shaft 20 in through housing 10.
The front end of the 1st running shaft 21 is externally given prominence to compared with front shroud 12A, at rotary driving sources such as this protruding terminus connecting engines.In addition, the rear end of the 2nd running shaft 22 is externally given prominence to compared with back cover 12B, links the live axle of hydraulic control pump 80 at this protruding terminus.Hydraulic control pump 80 utilizes the rotation of input shaft 20 to carry out work, to the deflection angle adjustment member supply working oil of swash plate 35A, 35B as aforementioned.
Be provided with in the outside of tapered roller bearing 26A, 26B and make the end of input shaft 20 be projected into outside and bearing support member 14A, 14B of the ring-type of tapered roller bearing 26A, 26B being fixed in thrust direction.In addition, bearing support member 14A utilizes bolt to fix with the state of the inner circumferential being embedded in front shroud 12A, and bearing support member 14B utilizes bolt to fix with the state of the inner circumferential being embedded in back cover 12B.
Cylinder body 31A rotates integratedly to enable the end face of the side facing with middle casing 13 state closely sealed with valve block 34A slidably and the 1st running shaft 21.Cylinder body 31B rotates integratedly to enable the state closely sealed with valve block 34B slidably with the end face of the facing side of middle casing 13 and the 2nd running shaft 22.Each cylinder body room 32A, 32B of cylinder body 31A, 31B are communicated in suction port 51A, 51B and ejiction opening 61A, 61B of valve block 34A, 34B off and on via the end face opening by middle casing 13 side of cylinder body 31A, 31B.
At this, each valve block 34A, 34B offer suction port 51A, 51B of a cocoon shape respectively.In addition, on each valve block 34A, 34B, opening has ejiction opening 61A, 61B of two cocoon shapes respectively.The reason that each valve block 34A, 34B are respectively equipped with two ejiction openings 61A, 61B is to reduce pressure pulsation, the pressure loss.The pressure oil gushed out from these two ejiction openings 61A, 61B is exported to outside after interflow, downstream.
Middle casing 13 is provided with two suction passages 53A, 53B for importing working oil respectively to suction port 51A, 51B of valve block 34A, 34B.A suction port 52 of the outer side surface opening of two comfortable middle casings 13 of suction passage 53A, 53B is arranged towards each valve block 34A, 34B branch respectively.And, each end of two suction passages 53A, 53B with both ends of the surface 13A, the 13B of the configured openings of cocoon shape in middle casing 13, to be communicated with the suction port 51A of valve block 34A, the suction port 51B of valve block 34B respectively.
In addition, middle casing 13 is provided with ejection stream 60A, 60B of two systems, and this ejection stream 60A, 60B are used for the pressure oil sprayed from the ejiction opening 61A of valve block 34A and the ejiction opening 61B of valve block 34B being corresponded respectively to pump unit 30A, 30B and externally deriving independently of one another.
Fig. 2 is the structural drawing representing middle casing 13, and (A) is side view, and (B) is axial end view drawing.
Ejection stream 60A, 60B of two corresponding with two pump unit 30A, 30B respectively systems are configured on middle casing 13 in the mode be separated from each other in the axial direction.That is, ejection stream 60A is configured in the front side close to pump unit 30A, and ejection stream 60B is configured in the rear side close to pump unit 30B.
As aforementioned, valve block 34A, 34B of each pump unit 30A, 30B are respectively equipped with two ejiction openings 61A, 61B.Therefore, the ejection stream 60A of one system of middle casing 13 is configured to following stream: the one end on the flow direction of pressure oil has two inflow entrance 62A, the other end on the flow direction of pressure oil has an outflow opening 63A, and the midway on the flow direction of pressure oil has merging part 66A.The ejection stream 60B of another system of middle casing 13 is configured to following stream: the one end on the flow direction of pressure oil has two inflow entrance 62B, the other end on the flow direction of pressure oil has an outflow opening 63B, and the midway on the flow direction of pressure oil has merging part 66B.
Two inflow entrance 62A are entrances that the pressure oil sprayed for two ejiction opening 61A from pump unit 30A respectively flows into, two inflow entrance 62B are entrances that the pressure oil sprayed for two ejiction opening 61B from pump unit 30B respectively flows into, and inflow entrance 62A, 62B are made up of the circular port towards axially open respectively.Outflow opening 63A, a 63B make pressure oil flow out to outside outlet, and it is made up of the circular port towards direction orthogonal to the axial direction respectively.Thus, two inflow entrance 62A of the ejection stream 60A of a system are opened on an end face 13A axially of middle casing 13 respectively, and two inflow entrance 62B of the ejection stream 60B of another system are opened on the other end 13B axially of middle casing 13 respectively.
In addition, ejection stream 60A, 60B outflow opening 63A, 63B separately of two systems are opened on towards the outer side surface 13C in the direction orthogonal with the axis of middle casing 13.Merging part 66A is for making the pressure oil flowed into from described two inflow entrance 62A collaborate and the part of the described outflow opening 63A that leads, and merging part 66B is for making the pressure oil flowed into from described two inflow entrance 62B collaborate and the part of the described outflow opening 63B that leads.In addition, ejection stream 60A, 60B outflow opening 63A, 63B separately of two systems delivery outlet be connected with the stream of not shown oil hydraulic circuit of being serial type oil hydraulic pump 1.
Be formed in ejection stream 60A, 60B of two systems of middle casing 13 the overlap region part existed from overlapping each other during end on observation in the axial direction dividually.In (B) of Fig. 2, overlap region part R1, R2 are illustrated with hacures.
As with reference to illustrating before Fig. 1, suction passage 52A, 52B, ejection stream 60A, 60B collect and are configured on middle casing 13 (the intermediate portion region of housing 10).Ejection stream 60A, 60B of two systems are wherein configured in and are separated from each other vertically but close position.Therefore, there is overlap region part R1, the R2 from overlapping each other during end on observation.
Close to each other like this and be formed with the part of ejection stream 60A, 60B of two systems, consider security intensity and need to guarantee to be enough to stand the wall thickness (required wall thickness) using pressure in advance between ejection stream 60A, 60B.In addition, for each pump unit 30A, 30B from ejiction opening 61A, 61B of valve block 34A, 34B to the flow path cross sectional area of the outlet (outflow opening 63A, 63B) of ejection stream 60A, 60B, expect to expand as much as possible in advance to reduce the pressure loss.
Therefore, two systems ejection stream 60A, 60B need to meet predetermined size condition in advance from overlap region part R1, the R2 of overlap during end on observation.Therefore, in this serial type oil hydraulic pump 1, first, overlap region part R1, the R2 of ejection stream 60A, 60B of two systems open the shortest size between the inwall making ejection stream 60A, 60B of two systems (between the inwall of namely most proximal portion size) SA with sky is that the mode at predetermined above (more than required wall thickness) such interval configures.
In addition, on this basis, merging part 66A, the 66B of ejection stream 60A, 60B are configured in than overlapping area part R1, R2 near the side of outflow opening 63A, 63B.Namely, being positioned at of ejection stream 60A is configured to than the part of merging part 66A near the side of inflow entrance 62A two streams 64A, 65A being communicated with two ejiction opening 61A of valve block 34A respectively, sprays being positioned at of stream 60B and is configured to than the part of merging part 66B near the side of inflow entrance 62B two streams 64B, 65B being communicated with two ejiction opening 61B of valve block 34B respectively.Thus, overlap region part R1, R2 are formed by a stream in two streams 64A, 65A and a stream in two streams 64B, 65B.
That is, for overlap region part R1, be set as it being only that an a stream 65A and stream 65B overlaps each other in the axial direction.In addition, for an overlap region part R2, be set as it being only that an a stream 65A and stream 64B overlaps each other in the axial direction, for another overlap region part R2, be set as it being only that an a stream 64A and stream 64B overlaps each other in the axial direction.
Like this, in the scope (upstream side of ejection stream 60A, 60B) comprising overlap region part R1, R2, owing to forming ejection stream 60A and ejection stream 60B by two streams 64A, 65A and two streams 64B, 65B respectively, therefore, it is possible to the sectional area of each stream is set to about half.Thus, the sectional area of the stream of each overlap region part R1, R2 can be made to become half respectively.Thereby, it is possible to the longest dimension SB between the stream inwall of reduction overlap region part R1, R2.Its result, contributes to the total length shortening serial type oil hydraulic pump 1.
Such as, when by when when being made up of ejection stream 60A, 60B of each system respectively a stream, required flow path cross sectional area S is set to 100, when the stream amassing s by two same cross-sectional forms identical flow path cross sectional area S (=100), " S=2s ", therefore, each flow path cross sectional area s in these two streams is respectively half, namely 50.
Compare when the cross section of stream is circular, due to " sectional area=two sectional area be added time one ", therefore, if the radius of stream when one is set to R, the radius of each stream when two is set to r, then r=R/ √ 2 ≒ R × 0.7.That is, two time the radius of stream or diameter can than one time the radius of stream or diameter little by about 30%.
Thus, by ejection stream 60A, 60B of two systems are set to a stream two streams 64A, 64B and a stream in two streams 65A, 65B from overlap region part R1, the R2 of overlap during end on observation, compared with the flow diameter of overlap region part when being formed the sectional area identical with the sectional area sum of two streams by a stream, the flow diameter of overlap region part R1, R2 can be reduced.Therefore, it is possible to reduce the longest dimension SB between stream inwall while ensuring more than required wall thickness by the shortest size SA between stream inwall.Thereby, it is possible to seek the axial dimension SC shortening middle casing 13.
The serial type oil hydraulic pump of present embodiment has structure as described above, below, is described its work.
First, when rotary driving source work such as making motor makes input shaft 20 rotate to drive input shaft 20, the cylinder body 31A of pump unit 30A and the cylinder body 31B synchronous rotary of pump unit 30B.When cylinder body 31A, 31B rotate, each plunger 33A, 33B to-and-fro motion in cylinder body room 32A, 32B engaged with each piston shoes 39A, 39B of being slidingly contacted at swash plate 35A, 35B.Thus, working oil is sucked by the suction port 52 from middle casing 13, is inhaled into cylinder body room 32A, 32B of cylinder body 31A, 31B by suction port 51A, 51B of suction passage 53A, 53B and valve block 34A, 34B.
The working oil being drawn into cylinder body room 32A, 32B is this time pressurizeed by plunger 33A, 33B, become pressure oil, be ejected into outside by ejection stream 60A, 60B of ejiction opening 61A, 61B and middle casing 13, be supplied to the hydraulic equipment being connected to ejection stream 60A, 60B.
When the deflection angle change of swash plate 35A, 35B, suitably adjust the path increment of each plunger 33A, 33B.Thereby, it is possible to the flow of pressure oil that variable control sprays from each pump unit 30A, 30B.
In addition, in the above-described first embodiment, the situation that ejection stream 60A, 60B of two systems are set to a stream two streams 65B, 65A and a stream in two streams 64B, 64A from overlap region part R1, the R2 of overlap during end on observation is illustrated.But, be not limited thereto, as long as overlap region part R1, R2 are formed by two streams 65B, 65A and two streams 64B, 64A, and now the flow diameter of this overlap region part R1, R2 is less than flow diameter when forming overlap region part by a stream.That is, also can be that the position making to be formed with two streams 64A, 65A and the position being formed with two streams 64B, 65B overlap each other from during end on observation.
(the 2nd mode of execution)
Fig. 3 is the structural drawing of the middle casing of the serial type oil hydraulic pump representing the 2nd mode of execution, and (A) is side view, and (B) is axial end view drawing.In addition, identical reference character marked to the constituting component same with the 1st mode of execution shown in Fig. 2 and omit the description.
The serial type oil hydraulic pump of the 2nd mode of execution is the structure of the middle casing only changing the 1st mode of execution.Thus, the valve block of each pump unit is respectively equipped with two ejiction openings 61A, 61B in a same manner as in the first embodiment.
On middle casing 113, be provided with ejection stream 160A, 160B of two systems in the axial direction dividually.Stream 166A, a 166B that ejection stream 160A, 160B of each system have inflow entrance 162A, 162B and outflow opening 163A, 163B respectively by the two ends on the flow direction of pressure oil are formed.
Inflow entrance 162A, 162B are the entrances flowed into for the pressure oil interflow of two ejiction opening 61A, 61B ejections from each pump unit 30A, 30B.This inflow entrance 162A, 162B are opened on end face 13A, 13B axially of middle casing 113 with cocoon shape.
In addition, outflow opening 163A, 163B is for the pressure oil flowed into from inflow entrance 162A, 162B being exported to outside outlet.This outflow opening 163A, 163B are opened on towards the outer side surface in the direction orthogonal with the axis of middle casing 113 in the mode of circular hole.And, be configured to from inflow entrance 162A, 162B to stream 166A, 166B of outflow opening 163A, 163B the stream being bent into right angle.
Now, the overlap region part R1 from overlap during end on observation (dash area of (B) of Fig. 3) the shortest size SA opened with sky between the inwall making ejection stream 160A, 160B of two systems of ejection stream 160A, 160B of two systems be predetermined more than the mode at (more than required wall thickness) such interval configure.In addition, the stream sectional dimension T1 be configured on direction orthogonal to the axial direction comprising the scope of overlap region part R1 is greater than the stream of the long round section (also comprising elliptic cross-section) of axial sectional dimension T2.Thus, with formed the situation of stream with circular cross-section compared with, the axial cross section size of stream can be reduced.
Its result, in the part R1 of overlap region, can reduce the longest dimension SB between stream inwall while ensuring more than required wall thickness by the shortest size SA between stream inwall.Therefore, it is possible to seek the axial dimension SC shortening middle casing 113, the total length shortening serial type oil hydraulic pump 1 can be contributed to.
Adopt at least one mode of execution described above, by the merging part 66A of ejection stream 60A, 60B of two systems be formed on middle casing 13, the position of 66B being set in the position than overlapping area part R1, R2 downstream (side close to outflow opening 63A, 63B), in the scope comprising overlap region part R1, R2, forming ejection stream 60A by two streams 64A, 65A, be made up of ejection stream 60B two streams 64B, 65B.Thus, compared with situation about being made up of a stream with ejection stream 60A, 60B, the sectional area of each stream can be made to become about half when being made up of two streams.In addition, at each overlap region part R1, R2 place, a stream in two streams 65B, 65A and a stream in two streams 64B, 64A will can be set to from the stream of overlap during end on observation.
Thus, each overlap region part R1 can be made, the flow path cross sectional area of R2 becomes half respectively, its result, at part R1 place, overlap region, can reduce the longest dimension SB between stream inwall while ensuring more than required wall thickness by the shortest size SA between stream inwall.Therefore, it is possible to seek the axial dimension SC shortening middle casing 113, the total length shortening serial type oil hydraulic pump 1 can be contributed to.
Be illustrated several mode of execution of the present invention, but these mode of executions proposing as an example, is not be intended to limit scope of invention.These mode of executions can be implemented in other various modes, can carry out various omission, replacement, change within a range not departing from the gist of the invention.These mode of executions and distortion thereof are included in scope of invention, purport, are similarly included in invention described in claims and its equivalent scope.
Claims (5)
1. a serial type oil hydraulic pump, it has:
Housing;
Two pump unit, they are arranged in this housing in the axial direction dividually;
Suction passage, it establishes on the housing, for importing working oil respectively to each suction port of described two pump unit; And
The ejection stream of two systems, they establish on the housing, respectively the pressure oil of each ejiction opening ejection from described two pump unit are exported to outside for each pump unit,
In the intermediate portion region of the intermediate portion of two the pump unit axially arranged dividually described in being located at of described housing, the ejection stream of described two systems configures in the axial direction apart from each other, wherein,
The described ejection stream of each system is configured to following stream:
Two ends on the flow direction of pressure oil possess:
At least two inflow entrances, it is towards axis, and the pressure oil respectively for the described ejiction opening ejection from each pump unit flows into; And
An outflow opening, it is towards direction orthogonal to the axial direction, for making pressure oil flow out to outside,
Further, the described midway of ejection stream on the flow direction of pressure oil of each system possesses merging part, and this merging part makes the pressure oil flowed into from described at least two inflow entrances collaborate and the described outflow opening that leads,
The overlap region part from overlap during end on observation of the ejection stream of described two systems, opens with sky and the shortest mode being of a size of predetermined above such interval between the inwall of the ejection stream of described two systems is configured,
Described merging part is configured in than described overlap region part near the side of described outflow opening, described ejection stream be positioned at two streams being configured to be communicated in respectively described two inflow entrances than the part of described merging part near the side of described inflow entrance.
2. serial type oil hydraulic pump according to claim 1, wherein,
Described overlap region part is formed by a stream in described two streams of the ejection stream of a system and a stream in described two streams of the ejection stream of another system.
3. serial type oil hydraulic pump according to claim 1 and 2, wherein,
Described two pump unit are formed by the cam-type axial piston pump that can change ejection capacity respectively, and this cam-type axial piston pump is disposed in axially, carrys out work by the synchronous rotary of the running shaft coaxially linked,
Described housing comprise two the shell main bodys holding described two pump unit respectively and the axial intermediate portion being sandwiched in described two shell main bodys as described in the middle casing in intermediate portion region of housing,
The valve block with two described ejiction openings of each pump unit formed by described cam-type axial piston pump is configured in the position contacted with the both ends of the surface axially of described middle casing,
Each inflow entrance of the ejection stream of described two systems is opened on the both ends of the surface axially of described middle casing respectively,
Each outflow opening of the ejection stream of described two systems is opened on the outer side surface towards direction orthogonal to the axial direction of described middle casing.
4. a serial type oil hydraulic pump, it has:
Housing;
Two pump unit, they are arranged in this housing in the axial direction dividually;
Suction passage, it establishes on the housing, for importing working oil respectively to each suction port of described two pump unit; And
The ejection stream of two systems, they establish on the housing, respectively the pressure oil of each ejiction opening ejection from described two pump unit are exported to outside for each pump unit,
In the intermediate portion region of the intermediate portion of two the pump unit axially arranged dividually described in being located at of described housing, the ejection stream of described two systems configures in the axial direction apart from each other, wherein,
The described ejection stream of each system is configured to
Two ends on the flow direction of pressure oil possess the stream of inflow entrance and an outflow opening, this inflow entrance is towards axis, and the pressure oil for the described ejiction opening ejection from each pump unit flows into, and this outflow opening is towards direction orthogonal to the axial direction, outside is flowed out to for making pressure oil
The overlap region part from overlap during end on observation of the ejection stream of described two systems open with sky that to make between the inwall of the ejection stream of described two systems the shortest and be of a size of predetermined more than the mode at such interval configure, and this overlap region part sectional dimension be configured on direction orthogonal to the axial direction sets be greater than the stream of the long round section of sectional dimension axially.
5. serial type oil hydraulic pump according to claim 4, wherein,
Described two pump unit are formed by the cam-type axial piston pump that can change ejection capacity respectively, and this cam-type axial piston pump is disposed in axially, carrys out work by the synchronous rotary of the running shaft coaxially linked,
Described housing comprise two the shell main bodys holding described two pump unit respectively and the axial intermediate portion being sandwiched in described two shell main bodys as described in the middle casing in intermediate portion region of housing,
The valve block with two described ejiction openings of each pump unit formed by described cam-type axial piston pump is configured in the position contacted with the both ends of the surface axially of described middle casing,
Each inflow entrance of the ejection stream of described two systems is opened on the both ends of the surface axially of described middle casing respectively,
Each outflow opening of the ejection stream of described two systems is opened on the outer side surface towards direction orthogonal to the axial direction of described middle casing.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2014194126A JP2016065482A (en) | 2014-09-24 | 2014-09-24 | Tandem type hydraulic pump |
| JP2014-194126 | 2014-09-24 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN105443338A true CN105443338A (en) | 2016-03-30 |
Family
ID=55553886
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510591462.XA Pending CN105443338A (en) | 2014-09-24 | 2015-09-16 | Tandem hydraulic pump |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JP2016065482A (en) |
| KR (1) | KR20160035978A (en) |
| CN (1) | CN105443338A (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP7025907B2 (en) * | 2017-12-01 | 2022-02-25 | 豊興工業株式会社 | Piston pump |
| CN114607577B (en) * | 2022-03-09 | 2023-09-08 | 西安航空学院 | Symmetrically arranged synchronous quantitative axial plunger pump and motor |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1062404A (en) * | 1990-12-10 | 1992-07-01 | 东北重型机械学院秦皇岛分校 | Multi-stage cascaded, open-loop, axial plunger pump |
| JPH08121328A (en) * | 1994-10-24 | 1996-05-14 | Kawasaki Heavy Ind Ltd | Tandem swash plate type hydraulic pump |
| JP2001140749A (en) * | 1999-11-17 | 2001-05-22 | Hitachi Constr Mach Co Ltd | Tandem type hydraulic pump |
| JP2001140754A (en) * | 1999-11-12 | 2001-05-22 | Nagatomo Ryutai Kikai Kenkyusho:Kk | Double piston pump |
| CN102434415A (en) * | 2011-12-02 | 2012-05-02 | 浙江大学 | Low-noise axial plunger pump based on indexing angle of pumps in series |
| CN103299073A (en) * | 2011-01-07 | 2013-09-11 | 洋马株式会社 | Multi-pump unit, tandem pump unit, and work vehicle |
-
2014
- 2014-09-24 JP JP2014194126A patent/JP2016065482A/en active Pending
-
2015
- 2015-09-14 KR KR1020150129712A patent/KR20160035978A/en unknown
- 2015-09-16 CN CN201510591462.XA patent/CN105443338A/en active Pending
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1062404A (en) * | 1990-12-10 | 1992-07-01 | 东北重型机械学院秦皇岛分校 | Multi-stage cascaded, open-loop, axial plunger pump |
| JPH08121328A (en) * | 1994-10-24 | 1996-05-14 | Kawasaki Heavy Ind Ltd | Tandem swash plate type hydraulic pump |
| JP2001140754A (en) * | 1999-11-12 | 2001-05-22 | Nagatomo Ryutai Kikai Kenkyusho:Kk | Double piston pump |
| JP2001140749A (en) * | 1999-11-17 | 2001-05-22 | Hitachi Constr Mach Co Ltd | Tandem type hydraulic pump |
| CN103299073A (en) * | 2011-01-07 | 2013-09-11 | 洋马株式会社 | Multi-pump unit, tandem pump unit, and work vehicle |
| CN102434415A (en) * | 2011-12-02 | 2012-05-02 | 浙江大学 | Low-noise axial plunger pump based on indexing angle of pumps in series |
Also Published As
| Publication number | Publication date |
|---|---|
| KR20160035978A (en) | 2016-04-01 |
| JP2016065482A (en) | 2016-04-28 |
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Effective date of abandoning: 20190705 |