CN1688812A - Long-piston hydraulic machines - Google Patents
Long-piston hydraulic machines Download PDFInfo
- Publication number
- CN1688812A CN1688812A CNA038205033A CN03820503A CN1688812A CN 1688812 A CN1688812 A CN 1688812A CN A038205033 A CNA038205033 A CN A038205033A CN 03820503 A CN03820503 A CN 03820503A CN 1688812 A CN1688812 A CN 1688812A
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- Prior art keywords
- piston
- cylinder
- wobbler
- hydraulic press
- plane
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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
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
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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
- F04B1/143—Cylinders
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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
- F04B1/122—Details or component parts, e.g. valves, sealings or lubrication means
- F04B1/124—Pistons
- F04B1/126—Piston shoe retaining means
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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
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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
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
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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
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
- F04B27/1036—Component parts, details, e.g. sealings, lubrication
- F04B27/109—Lubrication
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Reciprocating Pumps (AREA)
- Details Of Reciprocating Pumps (AREA)
- Hydraulic Motors (AREA)
Abstract
A smaller, lighter hydraulic pump or motor is provided with pistons, each of which has a body with a length approximately equal to the axial length of a corresponding cylinder in which the piston to-and-froly moves. A plurality of corresponding lubricating grooves which are circumferentially formed and radially traverse the wall of each cylinder are respectively positioned at positions which are always closed by the axial cylindrical body of each corresponding piston during the whole travel. The lubricating grooves are connected with one another to form a continuous lubricating channel totally positioned in the cylinder, and not connected by the input or output channels of fluid but supplemented by the blowby entering from the valve end of each cylinder. A plurality of sealing parts respectively positioned near the opening of each cylinder provide strong sealing and nearly eliminate the blowby coming from the lubricating channel, thus notably increasing the volumetric efficiency. The formed improved lubrication, combined with the only spring biasing holddown component, can use a variable-angle swash cam arrangement, which does not need not only a dogbone part on the outer end of the piston but also an ordinary swinger which can only nutate.
Description
Technical field
The present invention relates to have the hydraulic pump/motor machine of reciprocating elongated piston in cylinder, relate in particular to a kind of system that lubricated these pistons keep in touch simultaneously that is used between the wobbler of the head of these pistons and described pump/motor.
Background technique
Oil hydraulic pump and motor are known and widely used, have be installed in form in the cylinder body and around the rotation axis of driving element with the reciprocating piston in the corresponding cylinder body of the first radial distance circumferential arrangement.Many in these pump/motor machines have a variable displacement ability; And they are two kinds of basic designs normally: (a) piston in the cylinder body that rotates against tilting changeably but otherwise fixing wobbler to-and-fro motion or (b) piston in stationary housing against the wobbler to-and-fro motion of tilting and rotating changeably, described wobbler separates usually, is included in nonrotational (but nutating) rocker that slides on (with nutating) rotor surface of rotation.Though the present invention can be used for this two kinds of designs, it is particularly useful for the improvement of a kind of type machine in back, and this paper also describes and is this kind situation.
Though have that the hydraulic press of stationary housing can make than those must support and protect the machine of heavy rotary cylinder-block lighter, littler, the installation of wobbler rocker and support a big problem always.For high pressure/high-speed applications, rocker must be can the mode along the non-circular path relative movement that changes supporting between nonrotational piston and rocker.And the machine of this stationary housing uses " dog bone " formula extension rod (that is, having the bar of two spheric ends) so far, an end of each piston that interconnects and nutating but the plane of the rocker that do not rotate.A spheric end of described dog bone shape part is installed in the head end of piston pivotally, and common " sliding shoes " formula element that another spheric end is installed usually pivotally covers, and described " sliding shoes " formula element must be always against the wobbler rocker.These described elements have increased the manufacturing complexity and the cost of wobbler of the rotation of these machines greatly.
Dog bone shape bar also be used to sometimes to interconnect each piston an end and have the wobbler of inclination (but not rotating) of hydraulic press of the cylinder body of rotation.Yet, usually this back one type machine has omitted these dog bone shape parts, replaces the use elongated piston, each piston at one end have spherical head (and, usually cover by the common sliding die shoe of installing pivotally), described head contacts the nonrotational plane of wobbler effectively.These elongated piston design like this, i.e. the major component of the axial cylindrical shape body of each piston even also always supported by the wall of its respective cylinder when the range of piston.This additional support of these elongated piston is designed for when piston and rotates with its cylinder body, when piston head slides on the wobbler that tilts but do not rotate, guarantees the Side movement minimum of each spherical piston head.
Usually, these elongated piston are mainly lubricated by " blowby (blow-by) ", when promptly driving when the reciprocating piston driving or by high-pressure liquid, and the high-pressure liquid part of pressurized between the outer periphery of the wall of each cylinder and each piston body.This blowby just provides good lubricating when only enough fluid stream being arranged between the elongated cylinder of error permission casing wall and piston, and the blowby of sufficient to guarantee good lubrication influences the volumetric efficiency of pump or motor machine usually unfriendly.For example, 10 cubic inches machine can use the nearly blowby of 4 gallons of fluids of per minute.Though littler error can be used for reducing blowby usually, the reducing of these errors limited by the demand of sufficient lubrication.
Following public the present invention is intended to improve the volumetric efficiency of the machine of these elongated piston, guarantees the proper lubrication of (a) piston simultaneously and (b) is used to keep the simplified equipment that contacts between piston and the wobbler.
Summary of the invention
The invention discloses two kinds of different hydraulic presses.Two kinds of hydraulic presses have the preferred form of the wobbler of stationary housing and rotation/nutating.Yet [, those skilled in the art will appreciate that the present invention is equally applicable to have the cylinder body of rotation and the hydraulic press of the wobbler that do not rotate with the driving element of machine.] each disclosed machine can be used as pump or motor operations.A kind of machine has wobbler, and this wobbler is always when the driving element of machine rotates, with respect to the axis of driving element with the pre-determined tilt fixed angle, thereby make piston always with the predetermined stroke motion of maximum.The wobbler of another kind of open machine has the gradient that can change in mode well known in the art in whole angular range, thus the stroke of control piston in whole range of movement, the maximum value on each direction.
In each machine, each piston all is elongated, has axial cylindrical shape body portion, and is the same long with the axial length of reciprocating each cylinder therein on the described body portion preferred general.Preferably, each piston also has spheric end, by common pivot sliding shoes and better simply equipment, and the sliding contact of remaining valid with the plane of the wobbler of machine.The Side movement of first spheric end of the selection assurance piston of the axial length of each cylindrical piston body is minimum always.So even each piston extends to its range, still being supported on piston only in its respective cylinder partly is enough to guarantee it and the rotation/Side movement minimum of the extension spheric end of piston when the nutating planar slide contacts of wobbler.
According to the present invention, each cylinder in each machine cylinder body is provided with the associated lubrication groove that forms in the cylindrical wall at each cylinder.This lubricating channels is located like this, and promptly during to-and-fro motion, each associated lubrication groove keeps being sealed substantially by the axial cylindrical body of piston on the whole stroke of piston piston always in its respective cylinder.Preferably, each associated lubrication groove circumferentially forms, and each cylinder of crosscut radially.
And in the stationary housing of every machine, form other passages of a plurality of each described lubricating channels of interconnection.One of all lubricating channels and being interconnected in of another form a continuous lubrication channel in cylinder body.This continuous lubrication channel forms in cylinder body fully, each cylinder of crosscut preferably, and when cylinder when the rotation axis of driving element is placed in the middle, circumferentially placed in the middle with substantially the same radial distance.
[annotate: in order to help explaining the present invention, each piston is described as having axial cylindrical shape body portion and spherical head end, and each respective cylinder has valve end and opening head, and the spherical head end of each piston extends in outside the described opening head always.] in described preferred embodiment, above-mentioned continuous lubrication passage does not connect by fluid " input " or fluid " output " passage, but partially enclosed by the cylindrical body of piston always basically in machine run.In when work, this lubrication channel almost is full of the high-pressure liquid of initial blowby immediately, and described high-pressure liquid enters at the valve end of each cylinder, and the wall through each cylinder is driven between the piston only outer periphery partly with each then.This blowby keeps the high pressure in the continuous lubrication passage effectively always.Near a plurality of sealed members of opening end that lay respectively at each cylinder provide stronger sealing, basically eliminated the blowby between the opening head of each piston only part and each respective cylinder, thereby minimum blowby is overflowed through the opening end of cylinder from this lubrication channel.
Yet the lubricating fluid in the continuous lubrication passage of this sealing moves consistently, because along with the to-and-fro motion of piston, the pressure in each respective cylinder constantly changes.Promptly, when being reduced to low-pressure on the return stroke of the pressure in each cylinder at each piston, high-pressure liquid in the lubrication channel that other modes seal drives between the body outer periphery of the wall of each cylinder and each piston once more, enters the valve end of each cylinder that this pressure of experience reduces.Yet this secondary blowby is " loss " not, that is, it does not return storage tank, to replenish in the circulating liquid pressing system of sealing by the filling pump.On the contrary, the loop of sealing is returned in this secondary blowby immediately, need not use the filling pump, and the continuous lubrication passage of sealing is replenished by the similar high pressure blowby fluid that the valve end of each cylinder that increases from experience pressure enters immediately.
This described lubrication channel has significantly reduced blowby simultaneously for the high speed to-and-fro motion of piston provides suitable lubricating.In the successful operation process of commercial original shape machine constructed in accordance, blowby has reduced 90%.That is, the blowby of the common commercial hydraulic press of comparable specification experience is usually in the scope of per minute 4-5 gallon, and the blowby of original shape machine of the present invention experience is in the scope of per minute 0.5-0.7 gallon, thereby obviously increases the volumetric efficiency of hydraulic press of the present invention.
As mentioned above, the hydraulic press of stationary housing can manufacture littler and lighter than the hydraulic press of the common revolving block with similar specification.Because improved the lubricated of elongated piston,, and satisfy required high speed/high pressure specification in the automobile use so invention disclosed makes it can use these littler and lighter designs.
And what pay special attention to is the supporting component that the present invention has obviously simplified the variable rotary type wobbler of hydraulic press disclosed by the invention.Each supporting component of the present invention disclosed herein (a) has omitted the dog bone shape part between the rocker part of only nutating of wobbler of the outer end that is installed in each piston usually and common rotation/nutating, and (b) has omitted the rocker part of only nutating of the wobbler of common rotation/nutating.Alternatively, common sliding shoes is directly installed on the spheric end of each piston, and the minimum spring bias voltage of the sliding contact that is enough to when not having hydraulic coupling by the valve end at the cylinder of pump to remain valid, and keeps the effective sliding contact with the rotating part plane of wobbler.
The supporting mechanism of two kinds of simplification is disclosed.The supporting mechanism of first kind of simplification comprises by the unique pressure strip assembly around the helical spring bias voltage of the rotation axis circumferential arrangement of the driving element of pump.Second kind of supporting mechanism of the present invention is simpler, the common sliding shoes that only comprises the spheric end that is directly installed on each piston, the minimum bias of utilizing a plurality of springs to apply, each spring lay respectively between the valve end of the body portion of each respective pistons and each respective cylinder.And second supporting mechanism is than first kind of more difficult assembling, and the latter simplifies greatly, lighter and make more cheap.
The important change that the present invention proposes not only provides the hydraulic press lighter and littler than the common machines with similar specification, has bigger volumetric efficiency but also provide, and has reduced the weight and the size of machine simultaneously, and manufacture cost, and has simplified assembling.
Description of drawings
Fig. 1 is the diagrammatic cross-section fragmentary of hydraulic press, and hydraulic press has stationary housing and has the rotation of constant cant angle/nutating formula wobbler, shows to be included in the cylinder body and in the present invention at the interface of piston/wobbler.
Fig. 2 is the diagrammatic cross-section fragmentary of stationary housing of the hydraulic press of Fig. 1 of making along plane 2-2 and 3, has wherein for clarity sake omitted some parts.
Fig. 3 is the diagrammatic cross-section fragmentary of hydraulic press, and hydraulic press has stationary housing and has the rotation/nutating formula wobbler at variable tilted angle, shows once more to be included in the cylinder body and in the present invention at the interface of piston/wobbler.
Fig. 4 A and 4B are when the wobbler diagrammatic cross-section fragmentary that disclosed wobbler and piston sliding shoes hold down assembly in Fig. 1 and 3 that tilts+25 ° the time, some parts have wherein for clarity sake been removed, show head end, sliding shoes and the special packing ring of piston, and the relative position of spring bias voltage clamping element, described each sliding shoes of clamping element bias voltage makes its plane against wobbler; Figure among Fig. 4 A is along the intercepting of the direction of arrow of the plane 4A-4A of Fig. 3, and the figure among Fig. 4 B is along the plane 4B-4B intercepting of Fig. 4 A.
Fig. 5 A and 5B, 6A and 6B, 7A and 7B are respectively when wobbler during three other gradients, promptly+15 °, 0 ° and-25 °, and the view of the same parts shown in Fig. 4 A and the 4B.
Fig. 8 is similar to the only cylinder of another hydraulic press shown in Fig. 1 and 3 and the local amplification profile schematic representation of piston, but shows second embodiment that the spring bias voltage of piston of the present invention watt holds down assembly and more simplifies.
Embodiment
The operation that can increase that class hydraulic press of the present invention is known.So this operation is not described in detail.
Oil hydraulic motor
With reference to Fig. 1, oil hydraulic motor 10 comprises have a plurality of cylinders 14 stationary housing 12 of (only illustrating), the to-and-fro motion between the extended position of the retracted position of piston 16 and piston 16 ' of wherein corresponding a plurality of coupling pistons 16.Each piston has ballhead 18, and this ballhead is installed on the neck 20 of an end of elongated axial cylindrical shape body portion 22, shown in the preferred embodiment, the described body portion length with each respective cylinder 14 substantially is the same long.
Each ball-shaped end 18 is assemblied in the corresponding sliding shoes that slides on the plane 26 that forms on the surface of rotor 28, and described rotor is again with fixing on the driving element, promptly on the axle 30 of machine.Axle 30 is supported on the bearing in the hole 31 of cylinder body 12 centers.The plane 26 of fixed rotor 28 tilts with the 32 one-tenth intended maximum angular of axis (for example 25 °) with respect to live axle 30, is supported by suitable thrust bearing assembly 35.
Comprise a plurality of spool valves 34 (only illustrating) with bolt as the modular valve 33 of the lid on cylinder body 12 left ends, spool valve is regulated the fluid that enters cylinder 14 and discharge from cylinder 14.As mentioned above, disclosed each machine can be used as pump or motor operations.For the description of preferred embodiment, the wobbler machine of tilt fixing shown in Figure 1 is as motor operations.So, rotating the first half in each of live axle 30, enter the valve end of each respective cylinder 14 from the high-pressure liquid of inlet 36 through port 37, drive each respective pistons from its retracted position to its full extended position; And rotating the second half at each, along with each piston returns its complete retracted position, low-pressure fluid withdraws from from each respective cylinder through port 37 and fluid output 39.
Preferably, in mode well known in the art, fluid input 36 and outlet 39 are connected in the oil hydraulic pump (for example shown in Figure 3 and describe below pump 110) of coupling through suitable " loop " pipeline, thus hydrodynamic pressure always bias voltage ball-shaped end 18 and corresponding sliding shoes 24 against the plane 26.The continuous stretching, extension of each respective pistons and contraction cause rotor 28 to rotate, thus live axle 30.Plane 26 is fixed with allowable angle of inclination, thus when in loop through enter the mouth 36 and the flow velocity of outlet 39 hydraulic fluids that circulate hour, piston 16 to-and-fro motion are slower, it is slower to cause live axle 30 to rotate.Yet when circuit flow rate of fluid in loop increased, the to-and-fro motion of piston correspondingly increased, and the rotational velocity of live axle 30 also increases.When work under car speed or pressure (for example up to 4000rpm or 4000psi), the lubricated of piston becomes very important, and the blowby loss also may increase greatly.Cylinder body 12 improves by the present invention, thereby solves these lubrication needs and reduce the blowby loss.
Referring now to Fig. 1 and 2, the casing wall of each cylinder 14 is by the radially crosscut of associated lubrication groove 40 that wherein circumferentially forms.A plurality of passage 42 all lubricating channels 40 of interconnection, and in cylinder body 12, form continuous lubrication channel.Each corresponding lubricating channels 40 is sealed by the axial cylindrical shape body 22 of each respective pistons 16 in the whole stroke of each piston basically.That is, the wall of each associated lubrication groove 40 is played to seal in the outer periphery of each cylindrical body 22 always.Therefore, even when piston 16 during with the range to-and-fro motion, the continuous lubrication passage of all lubricating channels 40 that interconnect keeps sealing basically.Continuous lubrication passage 40,42 simply and economically forms in cylinder body 12, and this can understand by the schematic representation from Fig. 2 better, and wherein for clarity sake, the relative size of fluid channel and connecting passage is exaggerative.
When oil hydraulic motor 10 work, the lubricating channels 40 of all interconnection is almost filled by the high-pressure liquid blowby immediately, and described fluid 36 enters each cylinder 14 through ports 37 from entering the mouth, and between the outer periphery of casing wall and each piston 16 pressurized.The lubricating fluid loss of each lubricating channels 40 is subjected near the restriction around Sealing 44 of opening end of each cylinder 14.Yet, lubricating fluid appropriateness in the continuous lubrication passage of this sealing of lubricating channels 40 and flowing continuously, as when the reciprocating motion of the pistons in response to the result of " secondary " blowby of the variation in pressure in each half cycle of the rotation of piston motion and live axle 30.Pressure in each cylinder 14 is when the return stroke of each piston 16 is reduced to low-pressure, lubrication channel 40 in sealing, high-pressure liquid in 42 drives between the outer periphery of the wall of each cylinder 14 and the body portion 22 of each piston 16 once more, enters the valve end that experiences each cylinder 14 that this pressure reduces.
Yet those skilled in the art pay special attention to is this described secondary blowby not " loss " that enters in the cylinder 14.But, return the known sealing hydraulic fluid circuit of interconnection pump and motor immediately.And storage tank is not returned in this secondary blowby, so, needn't add to the loop hydraulic system by the filling pump.At last, the continuous lubrication passage 40,42 of sealing is replenished by the similar high pressure blowby fluid that the valve end of each cylinder that increases from experience pressure enters immediately.
As mentioned above, the continuous lubrication passage 42 from the sealing of all lubricating channels 40 that interconnect has minimum blowby loss.That is, the minimum fluid that leaks through the Sealing 44 of the end of each cylinder 14 from the continuous lubrication passage of this sealing is arranged.Yet any this minimum blowby is replenished by the similar blowby fluid that enters around the opposite end of each piston 16 immediately.
Above-mentioned lubricated configuration is not only obviously simplified, and can simplify the piston/wobbler interface equipment of hydraulic press similarly, makes and operating cost thereby further reduce.
In order intactly to describe oil hydraulic motor 10, the piston shown in Fig. 1/wobbler interface equipment only comprises that the rotor 28 that (a) utilizes common needle bearing and thrust-bearing to be installed on the live axle 30 is used to keep piston sliding shoes 24 to hold down assembly with the rotation of rotor 28 and the spring bias voltage of the nutating plane 26 stable simplification that contact with (b) always.[annotate: following two embodiments that in independent sector, describe the piston/wobbler interface assembly of simplification of the present invention in more detail.]
First embodiment who holds down assembly of the present invention as shown in Figure 1, comprises being positioned at around the axle 30 and being contained in cylinder body 12 around the circumferential helical spring 50 in the suitable slits 52 of formation of axis 32.Spring 50 bias voltages also circumferentially are positioned at the clamping element 54 around axle 30 and the axis 32.Clamping element 54 is provided with a plurality of openings, and each opening is around the neck 20 of respective pistons 16.Corresponding special packing ring 56 is between clamping element 54 and each piston sliding shoes 24.Each packing ring 56 has extension 58, and this extension contacts the outer periphery of corresponding sliding shoes 24, thereby keeps the plane 26 of sliding shoes and rotor 28 to be permanently connected to.
Owing to obviously simplified lubricated and piston/wobbler interface, above-mentioned oil hydraulic motor is efficiently, is easy to make and economical operation.
Variable hydraulic pump
Second preferred embodiment of hydraulic press of the present invention is shown in Figure 3.Variable hydraulic pump 110 comprises modular stationary housing 112, and this cylinder body is with identical with the cylinder body 12 of above-mentioned oil hydraulic motor 10 shown in Fig. 1.Cylinder body 112 has a plurality of cylinders 114 (only illustrating), the to-and-fro motion between the retracted position of piston 116 and variable extended position (maximum extension illustrates in the position of piston 116 ') of wherein corresponding a plurality of coupling pistons 116.Each piston has spherical head 118, and this head is installed on the neck 120 of elongated axial cylindrical shape body portion 122 1 ends, shown in the preferred embodiment, this body portion length with each respective cylinder 114 substantially is identical.Each spherical piston head 118 is assemblied in the corresponding sliding shoes 124, described sliding shoes slides on the plane 126 that forms on the surface of rotor 128, as below describing in more detail, this rotor is pivotally mounted to driving element promptly on the axle 130, and described axle is supported on the bearing in the hole 131 at cylinder body 112 centers.
In the mode of describing about oil hydraulic motor 10 above being similar to, changeable pump 110 also is provided with modular valve 133, this assembly uses bolt as the lid on modularization cylinder body 112 left ends, similarly, also comprise a plurality of spool valves 134 (only illustrating), the fluid that described valve regulation enters cylinder 114 and discharges from cylinder 114.
As mentioned above, disclosed each machine can be used as pump or motor operations.For the description of the preferred embodiment, variable-angle wobbler machine 110 shown in Figure 3 is as pump work, and live axle 130 is by prime mover (not shown) engine-driving of vehicle for example.So rotating in half in each of live axle 130, when each piston 116 moved to extended position, through 136 entry ports 137 that enter the mouth, low-pressure fluid sucked in each respective cylinder 114 from " loop " of the hydraulic fluid that circulates.Rotating down in half at each, the driving that each respective pistons 116 is returned its complete retracted position with high-pressure liquid from port one 37 through exporting 139 oil hydraulic circuits that import sealing.High-pressure liquid is sent into the oil hydraulic motor of coupling through suitable loop pipeline (not shown) then, for example, above-mentioned motor 10 causes the piston of coupling motor to move with the speed that the volume (galmins) along with the high-pressure liquid of carrying in a known manner in the art changes.
Referring again to modularization cylinder body 112, it is identical with cylinder body 12 structures of having described.That is, the cylindrical wall of each cylinder 114 is by the radially crosscut of associated lubrication groove 40 ' that wherein circumferentially forms.A plurality of passages 42 ' all lubricating channels 40 ' that interconnect, and in cylinder body 112, form continuous lubrication channel.The section of the cylinder body 112 of making along plane 2-2 seems to resemble fully the sectional view of the cylinder body 12 among Fig. 2.
In fact, above with reference to the equipment of the oil hydraulic motor shown in Fig. 1 and 2 10 at continuous lubrication passage 40 of the present invention, the 42 almost full contents of describing are equally applicable to the continuous lubrication passage 40 ' in the cylinder body 112 of oil hydraulic pump shown in Figure 3 110,42 ' operation comprises by making the lubricating fluid loss of each lubrication channel 40 ' minimum around Sealing 114 near the opening end that is positioned at each cylinder 114.Similarly, the mobile of lubricating fluid is appropriateness and continuous in the continuous lubrication passage 40 ', 42 ' of sealing, during as reciprocating motion of the pistons in response to the result of " secondary " blowby of change pressure in every half turn of piston motion and each live axle 130.Certainly, with different in the pump 110, when each piston 116 moves to extended position, in each cylinder 114 lower hydrodynamic pressure is arranged, and when each piston 116 because the high-pressure fluid source of pressurized when its extended position is driven into its complete retracted position, appears in the rotation of prime mover (not shown) by live axle 130 between the outer periphery of casing wall and each piston 116.
Yet those skilled in the art pays special attention to once more is this described secondary blowby not " loss " that enters in the cylinder 114.But, return the known sealing hydraulic fluid circuit of interconnection pump and motor immediately.That is, storage tank is not returned in this secondary blowby, so, needn't replenish the loop hydraulic system by the filling pump.And, though have from the continuous lubrication passage 40 ' of sealing, the minimum fluid that the Sealing 144 of 42 ' each cylinder 114 end of process leaks, but the blowby of any minimum is additional by the similar blowby fluid that enters around each the piston opposite end that increases from experience pressure immediately.
As previously mentioned, the present invention can simplify the wobbler equipment of machine, (a) omit the dog bone shape part between the rocker part be installed in each piston outer end and the only nutating of common rotation/nutating wobbler usually and (b) omitted rocker part itself and nonrotational rocker is installed in common required equipment on the rotation/nutating rotor portion of wobbler.
The axis 129 that rotor 128 winds perpendicular to axis 132 is installed on the live axle 130 pivotally.So when rotor 128 rotated with live axle 130, it can be changed to ± 25 ° from 0 ° (promptly vertical) with respect to the tilt angle of axis 130.In Fig. 3, rotor 128 tilts+25 °.This variable following control of inclination: rotor 128 determines that by the position of sliding collar 180 the described axle collar centers on live axle 130 and can move axially with respect to this axle around 129 pivot.Control link 182 connects the axle collar 180 and rotor 128, thereby the axle collar 180 causes rotor 128 to pivot around axis 129 in live axle 130 lip-deep axial motions.For example, when the axle collar 128 moves among Fig. 3 the right side, the gradient of rotor 128 from shown in+25 ° gradient returns 0 ° (promptly vertical), and then changes in-25 ° whole continuum.
When york piece 186 by the hinged of york piece control arm 188 during around the rotational of york piece axle 190, the axial motion of the axle collar 180 is subjected to the control of the finger shape plate 184 of york piece 186.York piece 186 is activated by the common lienar servomechanism (not shown) that is connected in yoke arms 188 bottoms.In the preferred embodiment, when all the other elements of york piece 186 all are enclosed in the modularization wobbler housing 192, and york piece 190 is when being supported in the bearing that is fixed in housing 192, and york piece control arm 188 is positioned at housing 192 outsides.
Should be noted also that wobbler rotor 128 by shadow connecting rod 194 balances, shadow connecting rod 194 is identical with control link 182 substantially and be connected in the axle collar 180 similarly, but in the position of the just in time opposite side of the axle collar 180.
The piston sliding shoes holds down assembly
Hydrodynamic pressure is along the direction of rotor 128 biases piston 116 consistently, and thrust plate 198 is used to bear this load.Yet, to use under the required operating rate (for example 4000rpm) at automobile, necessary additional bias load is with constant contact between the plane 126 of guaranteeing piston sliding shoes 124 and rotor 128.Consider that the present invention has omitted common dog bone shape part and omitted common rocker and required mounting assembly, hydraulic variable machine of the present invention can provide this additional bias by using two simple spring bias voltages to hold down assembly, and has described about the oil hydraulic motor among Fig. 1 above first component class is similar to.
(a) single spring bias voltage holds down assembly
The following content of the first embodiment of the invention that is used to hold down assembly continues with reference to Fig. 3, but now also (a) is with reference to Fig. 4 A, the figure shows when when the direction of arrow is seen, enlarged view along the plane 4A-4A of Fig. 3 intercepting, and (b) with reference to Fig. 4 B, the figure shows the amplification of same view shown in Figure 1, wherein for clarity sake removed some parts.
Being used for holding down assembly of pump 110 comprises and is positioned at around the axle 130 and is contained in cylinder body 112 around the circumferential helical spring 150 in the suitable slits 152 of formation of axis 132.Helical spring 150 bias voltages are also around the clamping element 154 of axle 130 and axis 132 circumferential arrangement.Clamping element 154 is provided with a plurality of circular opens 160, and each opening is around the neck 120 of respective pistons 116.A plurality of special packing rings 156 are placed on respectively between clamping element 154 and each the piston sliding shoes 124.Each packing ring 156 has the extension 158 of the corresponding sliding shoes of contact 124 outer peripherys, thereby keeps the plane 126 of sliding shoes and rotor 128 to be permanently connected to.
Along with the changes in pitch of machine works rotor 128, the above-mentioned position component that wobbler and piston sliding shoes hold down assembly changes mutually.A plurality of gradients that these relative positions change with rotor 128 illustrate, promptly among Fig. 4 A and the 4B+25 °; Among Fig. 5 A and the 5B+15 °; Among Fig. 6 A and the 6B 0 °; Among Fig. 7 A and the 7B-25 °.[annotate: person of skill in the art will appreciate that each piston sliding shoes 124 has usual pressure balance cavity placed in the middle on sliding shoes 124 planes on the plane 126 that contacts rotor 128; and each corresponding sliding shoes cavity is connected with piston channel 164 by suitable sliding shoes groove 162, guarantees that the hydrodynamic pressure of sliding shoes/rotor interface equals the hydrodynamic pressure of each piston 116 head always.Because piston channel 164 is through the center of the spherical head 118 of each piston 116, the position of groove 164 can be used for understanding the relative movement of each parts that holds down assembly.]
With reference to the relative position of these parts under 0 ° of gradient shown in Fig. 6 A and the 6B, each piston channel 164 (at the center of each spherical head 118 of each piston 116) has the same radial position with respect to each the respective circular opening 160 in 154 of holding down assembly.From the view of gradient shown in other of wobbler rotor 128 as can be seen, the institute outside 0 ° is gradient down, and the relative radial position of each piston channel 164 is for each opening 160 difference, and the relative position of each special packing ring 156 is also different.
Must recognize that under each the wobbler gradient shown in these, along with rotor 128 rotates and a complete week of nutating, the different relative positions self of each of 9 openings 160 change consistently under each gradient of these gradients.For example, under 25 ° of the gradients shown in Fig. 4 A, if in each week of rotor 128, observe only pass through clamping element 154 the top (promptly, position at 12:00) motion that opening 160 occurs, the relative position of seeing parts in open top 160 will change continuously, thereby mate the relative position shown in each opening in other 8 openings 160.
That is, at (for example under-25 ° shown in Fig. 7 A) under the gradient outside 0 °, in each revolution of rotor 128, each special packing ring 156 slides on the surface of clamping element 154, and simultaneously, each sliding shoes 124 slides on the plane 126 of rotor 128; And each of these parts through in each of each a plurality of position that can see of other 8 openings 160 with respect to its own opening 160 variations.These relative movement are maximum down at ± 25 °; Each is respectively along circular path (looking like twisted-pair cable, i.e. " 8 font "), and described path is along with the horizontal position varying dimensions of each piston 116 in the angle gradient of wobbler rotor 128 and the stationary housing 112.
So, be the correct contact between the plane 126 of guaranteeing each corresponding sliding shoes 124 and rotor 128, in a preferred embodiment, size is selected on the border of each opening 160 like this, promptly rotor 128 each the revolution in and for rotor 128 the institute gradient, keep in touch with the over half of surface of each special packing ring 156 always on the border of opening 160, and the relative position on the border of this can be from each accompanying drawing of Fig. 4 A to Fig. 7 A special packing ring 156 and each opening 160 is found out.Can find out from accompanying drawing that circular boundary is preferred for each opening 160.
At last, attention is that suggestion utilization enhancing thermoplastic resin material is made each sliding shoes 124 and mated special packing ring 156 accordingly.These matching blocks also can be combined into a thermoplasticity sliding shoes/washer combinations, and wherein the sliding shoes part is made like this, and promptly it forms around the spherical head 118 of each piston 16 ', 22.Similarly, by using the thermoplastic resin that strengthens, can obviously reduce the cost and the complexity of thrust bearing assembly 35.
(b) many springs bias voltage holds down assembly
It is quite simple to be difficult to second embodiment who holds down assembly of the present invention that assembles slightly, and not too expensive.This second embodiment schematically illustrates in Fig. 8, and this figure is the local amplification view of single piston of another hydraulic press 210 of the present invention.Piston 216 is positioned at the modularization stationary housing 212 of cylinder 214, and the latter is by the associated lubrication groove 40 that wherein circumferentially forms " radially crosscut.With with the identical mode of above-mentioned other hydraulic presses, lubricating channels 40 " similar interconnection trench in other cylinders by a plurality of passages and machine, the continuous lubrication channel of formation cylinder body 212 in; Similarly, be positioned at around Sealing 244 near the opening end of each cylinder 214, thereby make each lubricating channels 40 " lubricating fluid loss minimum.
Unique difference in stationary housing 212 and Fig. 1 and 3 between the disclosed modularization cylinder body is that stationary housing 212 does not comprise big axial circumference helical spring, does not also comprise the axial circumferential gap of fixing described spring.
Though do not illustrate, the modularization stationary housing 212 of hydraulic press 210 can be connected in the swashplate assembly (as shown in Figure 1) of modularization tilt fixing or the swashplate assembly (as shown in Figure 3) of modularization variable-angle; But under any situation, hydraulic press 210 provides simpler and has held down assembly.Particularly, holding down assembly of this embodiment only comprises the corresponding pot type piston sliding shoes 224 that is used for each piston 216, and corresponding helical spring 250; The latter also links to each other with each respective pistons 216.
Each piston sliding shoes 224 is similar at the above-mentioned first common sliding shoes shown in holding down assembly, and similarly, be installed on the spherical head 218 of piston 216, thereby on the plane 226 that forms on the surface of the wobbler rotor 228 of machine, slide to be similar to above-mentioned mode.Each helical spring 250 is circumferentially laid around the hydrovalve port 237 of the valve end of each respective cylinder 214 respectively, and is positioned at the body portion of each respective pistons 216.
And in above-mentioned mode, each sliding shoes 224 slides on the plane 226 of rotor 228 with twisted-pair cable motion, and described motion is along with the horizontal position of each piston 216 and the rotor 228 changes in pitch size with respect to axis 230.When the normal operation of hydraulic press 210, sliding shoes 224 keeps in touch by the plane 226 of hydraulic coupling and wobbler.So the spring bias voltage that helical spring 250 provides only is a minimum value, but be enough to when the valve end of each respective cylinder 214 does not have hydraulic coupling, to keep effective sliding contact between each sliding shoes 224 and the plane 226.
The above-mentioned minimum bias that has been found that spring 250 not only is beneficial to assembling, and is enough to prevent run in the assembling process or minute dust and the metal fragment that occurs that wear and tear carried secretly.And, special concern be that this second embodiment only provides this essential function with some very cheap parts.
Above-mentioned pump/motor and foregoing other hydraulic presses of the present invention all provide lubricated and piston/wobbler interface, they are obviously simplified, and manufacturing is cheaper, by reducing the required part count of effective operation, increase volumetric efficiency, further Economy is provided.
Claims (15)
1. hydraulic press, have a plurality of reciprocally be installed in form in the cylinder body and circumferentially be arranged on piston in the cylinder of first radial distance around the rotation axis of driving element, each described piston has body portion and head end, each respective cylinder has valve end and opening head, the described head end of each described piston extends beyond described opening head always, and described piston also has the stroke that changes to predetermined maximum, and described improvement comprises:
Be formed on the associated lubrication groove in the cylindrical wall of each the described cylinder in the described cylinder body;
All described lubricating channels interconnection are to form continuous lubrication channel in described cylinder body; And
In the whole stroke of each described piston, each corresponding lubricating channels is sealed by the axial cylindrical shape body of each respective pistons substantially, thereby seals described continuous lubrication passage substantially always.
2. hydraulic press as claimed in claim 1, it is characterized in that the continuous lubrication passage of described sealing is formed entirely in the described cylinder body, each described cylinder of crosscut, and when described cylinder when the rotation axis of driving element is placed in the middle, circumferentially placed in the middle with identical substantially radial distance.
3. hydraulic press as claimed in claim 1 is characterized in that, also comprises near the sealed member the described opening head that is positioned at each described cylinder, is used for eliminating substantially the blowby between the described opening head of each described piston and each respective cylinder.
4. hydraulic press as claimed in claim 1 is characterized in that, the continuous lubrication passage of described sealing is only replenished by the blowby between the described valve end of the described body portion of each piston and each respective cylinder.
5. hydraulic press as claimed in claim 1, it is characterized in that the main movement of the lubricating fluid in the continuous lubrication passage of described sealing is that (a) piston motion, (b) change hydrodynamic pressure and (c) result one of at least of the blowby between the described valve end of each described piston and each respective cylinder in the described respective cylinder.
6. hydraulic press as claimed in claim 5 is characterized in that, with the loop combination of the hydraulic fluid that circulates, described loop is returned in the blowby between the described valve end of each described piston and each respective cylinder immediately, and need not to use the filling pump.
7. hydraulic press as claimed in claim 1, it is characterized in that, also comprise wobbler with plane, described wobbler has the gradient with respect to the described rotation axis of driving element, and during between described piston and the described wobbler all relatively rotate, the sliding contact of remaining valid in the described head end of each piston and the described plane of described wobbler, the described stroke of described piston is determined according to the gradient of described wobbler, and the described body portion of each piston has the axial cylindrical length that is enough to be supported in the described respective cylinder, thereby when guaranteeing in described stroke, to keep slide relative to contact with described plane always, the Side movement minimum of the described head end of described piston.
8. hydraulic press as claimed in claim 7 is characterized in that described cylinder body is fixed in the housing, and described wobbler rotates with described driving element, and comprises the rotor of rotation and nutating, and described plane is positioned on the described rotor.
9. hydraulic press as claimed in claim 8 is characterized in that the gradient of described wobbler is variable, the stroke of described piston according to described changes in pitch up to described predetermined maximum.
10. hydraulic press as claimed in claim 7 is characterized in that each piston has the spherical head end that is connected in described piston only by narrow neck portion, and described machine also comprises:
Be attached to the described spherical head end of each described respective pistons pivotally and during between described piston and the described plane all relatively rotate with the remain valid corresponding sliding shoes of sliding contact of the described plane of described wobbler; And
Be used for holding down assembly towards the described described sliding shoes of plane bias voltage of described wobbler.
11. hydraulic press as claimed in claim 10 is characterized in that, described holding down assembly comprises:
Towards described sliding shoes bias voltage and clamping element with a plurality of respective openings, the border of each the described respective openings in the described pressure strip is positioned near the described narrow neck portion of each respective pistons; And
Be assemblied in the described narrow neck portion respective gasket on every side of each piston between the corresponding sliding shoes with each of described pressure strip, each described respective gasket has the extension of cylindrical aligning, is used for circumferentially contacting each described corresponding sliding shoes;
When the described plane of described rotor tilted with respect to the described rotation axis of driving element, described packing ring and described pressure strip sliding contact changed relative its motion with the relative position in response to described sliding shoes.
12. hydraulic press as claimed in claim 11 is characterized in that, the border of each the described respective openings in the described pressure strip is designed to be permanently connected to outer periphery over half of each described respective gasket during described relative movement.
13. hydraulic press as claimed in claim 11 is characterized in that, described machine also is included in less than the helical spring of described first radial distance around the rotation axis circumferential arrangement of described driving element, is used for described pressure strip is biased in described packing ring.
14. hydraulic press as claimed in claim 10 is characterized in that, described holding down assembly only comprises:
When the described valve end of each respective cylinder does not have hydraulic coupling, be enough to keep the minimum spring bias voltage of the described effective sliding contact between the described plane of each described sliding shoes and described wobbler.
15. hydraulic press as claimed in claim 10 is characterized in that, described minimum spring bias voltage is provided by a plurality of springs, and each described spring lays respectively between the described valve end of the described body portion of each respective pistons and each respective cylinder.
Applications Claiming Priority (5)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US10/229,407 | 2002-08-28 | ||
| US10/229,407 US20040042910A1 (en) | 2002-08-28 | 2002-08-28 | Long-piston hydraulic machines |
| US10/647,557 | 2003-08-25 | ||
| US10/647,557 US20040042906A1 (en) | 2002-08-28 | 2003-08-25 | Long-piston hydraulic machines |
| PCT/US2003/026707 WO2004020827A2 (en) | 2002-08-28 | 2003-08-26 | Long-piston hydraulic machines |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1688812A true CN1688812A (en) | 2005-10-26 |
| CN100406726C CN100406726C (en) | 2008-07-30 |
Family
ID=32179426
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB038205033A Expired - Fee Related CN100406726C (en) | 2002-08-28 | 2003-08-26 | Long-piston hydraulic machines |
Country Status (10)
| Country | Link |
|---|---|
| US (1) | US20040042906A1 (en) |
| EP (1) | EP1546559A4 (en) |
| JP (1) | JP4350038B2 (en) |
| KR (1) | KR100659682B1 (en) |
| CN (1) | CN100406726C (en) |
| AU (1) | AU2003265692B2 (en) |
| BR (1) | BR0313882A (en) |
| CA (1) | CA2494996C (en) |
| MX (1) | MXPA05002282A (en) |
| WO (1) | WO2004020827A2 (en) |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103429936A (en) * | 2011-02-25 | 2013-12-04 | 昱曦机械高新科技有限公司 | Axial piston pump with pistons having metallic sealing rings |
| CN104153986A (en) * | 2014-07-21 | 2014-11-19 | 浙江沃尔液压科技有限公司 | Axial plunger hydraulic pump for hydraulic return stroke |
| CN112664386A (en) * | 2020-12-19 | 2021-04-16 | 王建设 | Pressure inclined type hydraulic power machine |
| CN114846238A (en) * | 2019-12-17 | 2022-08-02 | 米司创有限责任公司 | Axial piston pump with inclined plates |
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| MX2007015507A (en) * | 2005-06-15 | 2008-03-04 | Torvec Inc | Orbital transmission with geared overdrive. |
| RU2540348C2 (en) * | 2009-12-23 | 2015-02-10 | Бп Корпорейшн Норт Америка Инк. | Pump system and method for well reliquefaction |
| US8834133B2 (en) | 2010-08-05 | 2014-09-16 | Bp Corporation North America Inc. | Pumping device for fluids located at the bottom of a drilled well |
| ITPR20120004A1 (en) * | 2012-02-06 | 2013-08-07 | Lavorwash Spa | WASHING DEVICE USING A FLUID PRESSURE JET |
| CA2888027A1 (en) | 2014-04-16 | 2015-10-16 | Bp Corporation North America, Inc. | Reciprocating pumps for downhole deliquification systems and fluid distribution systems for actuating reciprocating pumps |
| CA2888028A1 (en) * | 2014-04-16 | 2015-10-16 | Bp Corporation North America, Inc. | Reciprocating pumps for downhole deliquification systems and pistons for reciprocating pumps |
| CN105697258A (en) * | 2014-11-25 | 2016-06-22 | 无锡市洗选设备厂 | Plunger pump structure for sand washing machine |
| US9828976B2 (en) * | 2015-01-30 | 2017-11-28 | Caterpillar Inc. | Pump for cryogenic liquids having temperature managed pumping mechanism |
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- 2003-08-26 CN CNB038205033A patent/CN100406726C/en not_active Expired - Fee Related
- 2003-08-26 EP EP03791793A patent/EP1546559A4/en not_active Withdrawn
- 2003-08-26 AU AU2003265692A patent/AU2003265692B2/en not_active Ceased
- 2003-08-26 BR BR0313882-8A patent/BR0313882A/en not_active IP Right Cessation
- 2003-08-26 WO PCT/US2003/026707 patent/WO2004020827A2/en active IP Right Grant
- 2003-08-26 CA CA002494996A patent/CA2494996C/en not_active Expired - Fee Related
- 2003-08-26 MX MXPA05002282A patent/MXPA05002282A/en active IP Right Grant
- 2003-08-26 KR KR1020057003519A patent/KR100659682B1/en not_active IP Right Cessation
- 2003-08-26 JP JP2004531484A patent/JP4350038B2/en not_active Expired - Fee Related
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103429936A (en) * | 2011-02-25 | 2013-12-04 | 昱曦机械高新科技有限公司 | Axial piston pump with pistons having metallic sealing rings |
| CN103429936B (en) * | 2011-02-25 | 2016-09-28 | 昱曦机械高新科技有限公司 | Piston has the axial poiston pump of metallic packing ring |
| CN104153986A (en) * | 2014-07-21 | 2014-11-19 | 浙江沃尔液压科技有限公司 | Axial plunger hydraulic pump for hydraulic return stroke |
| CN104153986B (en) * | 2014-07-21 | 2016-08-17 | 沃尔科技有限公司 | The axial plunger type hydraulic pump of hydraulic pressure backhaul |
| CN114846238A (en) * | 2019-12-17 | 2022-08-02 | 米司创有限责任公司 | Axial piston pump with inclined plates |
| CN112664386A (en) * | 2020-12-19 | 2021-04-16 | 王建设 | Pressure inclined type hydraulic power machine |
Also Published As
| Publication number | Publication date |
|---|---|
| AU2003265692B2 (en) | 2007-05-17 |
| CA2494996A1 (en) | 2004-03-11 |
| AU2003265692A1 (en) | 2004-03-19 |
| EP1546559A4 (en) | 2011-03-09 |
| WO2004020827A2 (en) | 2004-03-11 |
| CN100406726C (en) | 2008-07-30 |
| US20040042906A1 (en) | 2004-03-04 |
| JP4350038B2 (en) | 2009-10-21 |
| CA2494996C (en) | 2008-10-28 |
| EP1546559A2 (en) | 2005-06-29 |
| WO2004020827A3 (en) | 2004-05-06 |
| MXPA05002282A (en) | 2005-08-18 |
| BR0313882A (en) | 2005-08-02 |
| KR100659682B1 (en) | 2006-12-21 |
| AU2003265692B8 (en) | 2004-03-19 |
| KR20050032623A (en) | 2005-04-07 |
| JP2006510833A (en) | 2006-03-30 |
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