CN101535641B - Pressure compensated pump - Google Patents

Abstract

A pump that includes a piston moveable along a first axis and an eccentric cam positioned about a second axis, wherein the second axis is substantially perpendicular to the first axis. The pump also includes an actuator positioned adjacent to the cam and configured to move the cam along the second axis. In addition, the pump further includes a cam-adjacent bearing positioned between the piston and the cam, wherein the cam-adjacent bearing remains positioned substantially along the first axis upon movement of the cam along the second axis.

Description

Pressure compensated pump

The cross reference of related application

The application requires to be called in the name of submitting to for 2006 09 month No. 12 interests of the U.S. Provisional Patent Application that pressure compensated pump, application number are 60/843,701, thus its full content is incorporated herein by reference.

Technical field

The present invention relates generally to oil hydraulic pump.More particularly, even if the present invention relates to still can keep the pump of constant horsepower output when fluctuation occurs the pressure when their operations place.

Background technique

Even if it is obtainable still can keeping the pump of constant horsepower output current when fluctuation occurs the pressure of their operations place.These pumps are designed to, and utilize conventionally and be input to a certain amount of horsepower of pump and the shaft horsepower amount of described pump is maximized by motor, and no matter the pressure of their operations place.Therefore, these pumps can not keep the pump phase specific energy of constant output horsepower with higher performance rate operation with other.

Typically, can keep the pump of constant horsepower output in the scope of relatively low pressure, to move and design for multiaxis.The pump that can move in higher pressure range on the other hand, can not keep along with the variation of the operating pressure of pump constant horsepower output.Typically, described high-pressure service pump is that a plurality of pumps that multistage pump and the main mechanism being changed between a plurality of pumps by utilization link together form.

Therefore, even if expectation provides the pump with novelty and the method that under high pressure still can keep constant horsepower output.Also need to provide the pump with novelty being formed by infinite stages (that is, its actual be single-stage pump).

Apart from the above, thus also expectation provides the pump that modularization is easily keeped in repair and maintenance cost is low.Further, expectation provides by making to be included in the total measurement (volume) of piston chamber wherein and minimizes the pump that makes its maximizing efficiency.

Summary of the invention

By provide in one embodiment of the invention a kind of pump can be very to degree meet above-mentioned requirements.Described pump comprises the piston that can move along the first axle.Described pump also comprises that wherein the second axle is basically perpendicular to the first axle about the eccentric cam of the second axle location.Described pump further comprises in abutting connection with cam orientation and is configured to along the final controlling element of the second axle wedge cam.In addition, described pump also comprises and is positioned at the nearly camshaft bearing of first between piston and cam (cam-adjacent bearing), and wherein, when cam moves along the second axle, the first nearly camshaft bearing keeps substantially along the first axle location.

A kind of method of process pump is provided according to another embodiment of the present invention.Described method comprises with the first pressure level and the first power output stage process pump.Described method also comprises the first pressure level of pump operation is transformed to large the second pressure level more than 6000psi.Described method further comprises along with pump is transformed to operation under the second pressure level and substantially keeps the first power output stage from operation under the first pressure level.

According to another embodiment again of the present invention, provide another kind of pump.Described pump comprises along the translating device of the first axle translation.Described pump also comprises the slewing gear rotating around the second axle, and wherein the second axle is basically perpendicular to the first axle.Described pump further comprises the actuating device for slewing gear is moved along the second axle.In addition, described pump also comprises the tourelle that can roll around the outer surface of slewing gear, wherein tourelle is positioned between translating device and slewing gear, and wherein when slewing gear moves along the second axle, tourelle keeps substantially along the first axle location.

The method of another kind of process pump is provided still according to still another embodiment of the invention.Described method comprises makes eccentric shape cam ring rotate around the first axle.Described method also comprises makes cam along the first axle translation.Described method further comprises along with cam is along the first axle translation and along the first axle holding position that is close to the bearing of cam.In addition, described method also comprises that the rotation along with cam promotes the piston of contiguous bearing location together with bearing.Described method further comprises along with cam keeps coming from the substantially invariable power output stage of pump along the first axle translation.

In order to understand better detailed description of the present invention, and in order to evaluate better the reality contribution to prior art, summarized quite widely specific embodiment of the present invention.Certainly, other embodiment of the present invention will be described below and form the theme of the claim that is additional to this.

In described scheme, before describing at least one embodiment of the present invention in detail, it should be understood that the present invention sets forth be not limited to following description in its application in or the configuration of illustrated CONSTRUCTED SPECIFICATION and parts in the accompanying drawings.Except the embodiment who describes, puts into practice and carry out in every way, the present invention can instantiation.To it should be understood that equally word, term and summary are all the objects in order describing as used herein, and should not to be considered to restriction.

Therefore, it should be appreciated by those skilled in the art, described open institute based on design can easily be used as the basis of the design of other structures, and for carrying out the method and system of several objects of the present invention.Therefore, importantly, be believed to comprise the claim of described equivalent structure within not departing from the scope of aim of the present invention and scope.

Accompanying drawing explanation

Fig. 1 illustrates according to the cross section of the pump of the first embodiment of the present invention.

Fig. 2 illustrates the stereogram of the internal cross section of the pump shown in Fig. 1.

Fig. 3 illustrates a part for the cross section of the pump shown in Fig. 1, and wherein camshaft is in complete travel position.

Fig. 4 illustrates a part for the cross section of the pump shown in Fig. 1, wherein camshaft in complete without stroke (destroked) position.

Fig. 5 illustrates three typical horsepower curves of illustrated pump in Fig. 1 to 4.

Fig. 6 illustrates according to the cross section of another embodiment's again of the present invention piston cartridge.

Fig. 7 is the panorama of the piston cartridge shown in Fig. 6.

Fig. 8 illustrates the transparent perspective view of the pump circle subassembly shown in the Fig. 2 that comprises three chucks and a lubricated chuck.

Fig. 9 illustrates second half transparent view of the pump circle subassembly shown in Fig. 8.

Figure 10 illustrates the stereogram of the typical equipments of the pump shown in Fig. 1.Embodiment

Below in conjunction with accompanying drawing, describe the present invention, wherein identical reference character represents identical member all the time.Fig. 1 illustrates according to the cross section of the pump 10 of the first embodiment of the present invention.As shown in Figure 1, pump 10 has radial design (relative with axial design) and comprises the motor 12 that is connected to pump shaft 14.Pump shaft 14 holds the spring assembly 16 with the first end of contiguous motor 12 and the second end of contiguous cam 17.

According to a particular embodiment of the invention, spring assembly 16 comprises the group cover of two, three or more springs.When using three springs, hard spring (that is, have high elastic constants and can produce the spring of large elastic force when compressed) is typically positioned at the right of the spring assembly 16 shown in more close Fig. 1.In addition, medium spring is positioned at the centre of spring assembly 16, and soft spring is positioned near cam 17.Three kinds of springs form progressive spring assembly 16 together, and described spring assembly is used to respect to the miscellaneous part positioning cam 17 in pump 10 as described below.According to a particular embodiment of the invention, each spring in a plurality of springs in spring assembly 16 all has different spring rate/elastic force.Yet, there are two structures with upper spring of identical springs rigidity/elastic force also within the scope of the invention.

In Fig. 1, spring assembly 16 is about contained spring guide rod 13 location.Contained spring guide rod 13 is positioned at inside, abutment pin 11 and the keep-spring assembly 16 of axle 14 concentrically substantially in Zhou14 center.Be positioned at the most close cam 17 spring assembly 16 end be cam sealing plug 15, described cam sealing plug 15 is designed to prevent that the liquid that just lubricates cam 17 is leaked on spring assembly 16.

Be in operation, motor 12 is mechanically connected on pump shaft 14 and cam 17 and makes both to rotate.According to a particular embodiment of the invention, cam 17 with about 3000 and approximately the rpm between 4000rpm rotate.Yet other rpm scope also within the scope of the invention.

As shown in Figure 1, pump shaft 14; By pair of bearings 18, supported.Shaft seal assembly 20 is located around pump shaft 14 and near the end of contiguous motor 12.Equally around pump shaft 14 location be a pair of axle saddle 24, in position, this will become clear by reference to accompanying drawing to the miscellaneous part that described axle saddle 24 is generally used for keeping pump 10.

What located the end of contiguous cam 17 is guide piston 22, described cam 17 and spring assembly 16 relative positionings, and described guide piston 22 is used as effectively along the final controlling element of the longitudinal axis A wedge cam 17 of pump shaft 14.According to a particular embodiment of the invention, the thrust bearing assembly of substantially spherical object (for example ball) or all elements 23 is as shown in Figure 1 positioned between guide piston 22 and cam 17, to promote bearing 17 with respect to the axial-rotation of guide piston 22.Substantially spherical object or thrust bearing assembly 23 typically can rotate along with the rotation of cam 17.

According to other specific embodiments of the present invention, guide piston 22 is along the longitudinal axis A of pump shaft 14, to extend and arrive the little bar of the point of locating against cam 17.According to described embodiment, guide piston 22 provides against the single-point contact of cam 17 and has not therefore had related torque arm.Therefore, cam 17 can not need to rotate relative to high rpm rotary seal.To replacing the situation of the embodiments of the invention of single-point contact with thrust bearing assembly 23 or substantially spherical object, be also the same.

Cam 17 has a plurality of grooves 26 that are formed on wherein, and as shown in Figure 1, described cam 17 is that combination saw dentation is also typically about the longitudinal axis A of cam eccentric (the described longitudinal axis is also the longitudinal axis of the pump shaft 14 shown in Fig. 1).That in each of the groove 26 shown in Fig. 1, hold is ball 28A, 28B, 28C, 28D.Each in ball 28A, 28B shown in Fig. 1,28C, 28D is all positioned between piston 30 and lube pistons 31 and with the central shaft of piston 30,31 in identical plane.Typically, lube pistons 31 permission lubricant oil are introduced in the inside of pump shaft 14, and piston 30 is configured to as displacement of fluid mechanism (being discussed below).According to a particular embodiment of the invention, be in operation, eccentric shape cam 17, ball 28A, 28B, 28C, 28D and pump shaft 14 all pass through motor 12 and rotate in the race ring 44 and 45 shown in Fig. 2 around the longitudinal axis A of pump shaft 14, and they combine as eccentric.

In Fig. 1, the mutual vertical array of ball 28A and 28B is in line and forms first pair of ball, and ball 28C and 28D also mutually vertical array be in line and form second pair of ball.The every pair of ball also with the piston 30 shown in Fig. 1 in one and lube pistons 31 in one be vertically arranged in a straight line.In every pair of ball, the relative longitudinal axis A location near pump shaft 14 of a ball (for example, 28A and 28D), and another ball (for example, 28B and 28C) in a pair of ball is relative to same axle location.Around longitudinal axis A rotating cam 17, ball 28A, 28B, 28C, 28D, axle saddle 24 and race ring 44 and 45 o'clock, it has formed eccentric, the deviation post of each in ball 28A, 28B, 28C, 28D contacts with piston 30 impact eccentric with lube pistons 31.

At eccentric and piston 30 when in lube pistons 31 one contacts, ball 28B, the 28C of the relative longitudinal axis A away from pump shaft 14 are by one that outwards promotes in eccentric and piston 30 or lube pistons 31, and ball 28A, the 28D of relatively close longitudinal axis A will allow another piston 30 and lube pistons 31 towards the inside rollback of longitudinal axis A.Eccentric and cam 17 complete total distance that a piston 30 while rotating advances (, piston stroke) and are determined with how many fluids and can flow through pump 10.Conventionally, the distance that piston 30 is advanced is longer, and the fluid that flows through pump 10 is just more.

Pump 10 shown in Fig. 1 also comprises oil tank 32 (that is, oil storage tank), suction filter 34, return tube 36, from the input machine oil groove 38 of oil tank 32 and the mobile pump delivery outlet 40 that holds to come the high pressure oil of self-pumping 10.Be in operation, piston chamber's (for example, pump chamber shown in Fig. 6 62) that machine oil is flowed through suction filter 34, flowed through and input machine oil groove 38 and flow into the piston 30 shown in neighborhood graph 1 from oil tank 32.Then piston 30 by pressure-acting the machine oil in piston chamber and discharge machine oil by pump delivery outlet 40.Yet other pump structure also within the scope of the invention.

Fig. 2 illustrates the stereogram of cross section of the inside of the pump 10 shown in Fig. 1.Cross section shown in Fig. 2 is perpendicular to the cross section shown in Fig. 1.Fig. 2's is also consistent with the cross section of pump circle subassembly 25 above.As shown in Figure 2, in the contiguous axle saddle 24 of two ball 28A, 28B of the either side of cam 17 and race ring 42 location.In two eccentrics 44,45 shown in the outside neighborhood graph 2 of race ring 42 one.Pre-eccentric device 44 is illustrated as the most proximal end that is positioned at cross section, then eccentric 45 be positioned at pre-eccentric device 44 after (that is, near motor 12).

As discussed below, pump 10 is pressure compensated pump, when cam 17 is suitably located with respect to pump shaft 14 and piston 30, pump 10 can carry the function being moved as pump 10 variation fluid flow and with pump 10, by any pressure of operation place, carried the fluid flow changing.According to specific embodiment of the present invention, and just as described below, pump 10 is configured to, the pressure by monitoring pump operation place and carry out himself output performance of optimization by the operation that utilizes force value to control himself.

By limiting, in order to judge the horsepower of pump, first make the fluid flow (for example, gpm) of efflux pump and the pressure of operation place of pump multiply each other, then make the value calculating divided by a constant.For example, when utilizing the motor of 1.5 horsepowers as motor 12 driven pump 10, typical preferred, with the rated horsepower level process pump that is similar to optimize its performance.Same typical preferred, even when the operating pressure of pump fluctuates, still can keep the rated horsepower level operation of pump to be similar to.

At present, on market, need a kind of like this pump: even when fluctuation occurs the pressure at pump operation place, pump also can keep reaching 10000psi scope and above constant horsepower output (that is the pressure compensated pump that, need to move with relatively high pressure).Yet current obtainable pressure compensated pump preferably also can only move in reaching 2000 to 5000psi scope.Equally, even at these relatively low pressure places, current obtainable pressure compensated pump is also complicated, expensive and heavy mechanism.

The obtainable pump moving within the scope of 10000+psi is at present multistage pump, and therefore continuous pressure compensation is not set.Definitely, whenever the operating pressure of the rising of pump impels when transforming or transitting to a new stage, these multistage pumps just experience the decline of output power.Whenever the operating pressure of the rising of pump impels while arriving the conversion of a new stage or transition, these multistage pumps just experience the decline of output power.In other words, these pumps and pressure compensated pump compare relative nullity.In addition, being used in the descending mechanism (step-down mechanism) comprising in complexity, costliness and heavy this pump is each stage elliptical gear plate and/or valve plate or non-loaded valve.

According to a particular embodiment of the invention, pump 10 is unlimited variable single-stage pressure compensation pump (that is, infinite stages), and it can move from the extremely about 10000psi of about 1psi and above any position.Illustrated in Fig. 1 and 2, it is relatively simple that the parts of pump 10 are designed to be, and by as described below, the operation of pump 10 is relative efficiencies.

Fig. 3 illustrates a part for the cross section of the pump 10 shown in Fig. 1, and wherein camshaft 17 is in complete travel position (that is, the position of the piston 30 of the most close shallow portion that is arranged in groove 26 of ball 28B and 28C).Fig. 4 illustrates a part for the cross section of the pump 10 shown in Fig. 1, wherein camshaft 17 in complete without travel position (that is, the position of the piston 30 of the most close deepest part that is arranged in groove 26 of ball 28B and 28C).Fig. 4 also illustrates the pilot pressure port (pilot pressure port) 46 of the high-pressure channel that is connected to pump 10.According to a particular embodiment of the invention, described pressure is used to control the position of guide piston 22.

When implementing embodiments of the invention, what it should be appreciated by those skilled in the art is, when cam 17 is located as shown in Figure 3 and passed through motor 12 (shown in Fig. 1) and rotate, the maximum stroke that piston 30 experience are allowed by pump 10 also provides maximum flow to keep given horsepower.On the other hand, when cam 17 is located as shown in Figure 4, the stroke of the minimum degree that piston 30 experience still allows pump 10 to be moved as planned.The position adjustment of following cam 17 will allow pump 10 to provide needed maximum horsepower at the operating pressure place of pump 10.

Fig. 5 illustrates three representational horsepower curves.Solid line is the horsepower data based on theoretical, and two survey data that dotted line is two typical two stage pumps based on not advancing along horsepower curve.According to a particular embodiment of the invention, the profile of cam 17 (profile) (, the curvature of groove 26) with the design of spring assembly 16 (, be included in the relative force that the spring in spring assembly 16 applies when pressurized) and the relation of guide piston power is together, and pump 10 is kept along the indicated horse power curve motion shown in Fig. 5.As above-mentioned record, although can use theoretical value, the shape of horsepower curve is typically judged via positive research.The formula of definition horsepower curve is that exponential function and utilizing in hundreds of data points that make the horsepower maximized different operating pressure of output of pump 10 and do not pick up under the same flow volume of pump 10 produces.

According to a particular embodiment of the invention, horsepower curve is level and smooth so that continuously.This considers that the groove 26 in cam 17 is also level and smooth and continuous.When pump 10 operation, guide piston 22 is applied to power on cam 17, and described power typically equals the pressure of operation place of pump 10 itself or is the function of the pressure of operation place of pump 10 itself.According to a particular embodiment of the invention, closed feedback loop signal is used for controlling guide piston 22 (discussing) below.According to another embodiment of the invention, can provide manually or automatically joining portion to control guide piston 22.Equally, those skilled in the art implement to become when of the present invention control clearly guide piston 22 other devices also within the scope of the invention.

Anyway control, the power being directly or indirectly applied on cam 17 by guide piston 22 is positioned at the substantially optimal position of the operating pressure of relative piston 30 in pump 10 by cam 17.In other words, cam 17 is positioned so that ball 28A, 28B, 28C, 28D impel piston 30 to the stroke distances that is provided for the flow rate of pump 10, the described basic optimization of flow rate for pump 10 rated horsepower of pump 10 at its operating pressure place.

Turn back to the discussion of Fig. 3 and 4, in the complete travel position shown in Fig. 3, pump 10 for example, is carried relatively high flow rate with relatively low pressure (, only a small amount of psi).Complete in travel position shown in Fig. 4, pump with relatively high pressure (for example, 6000 and 10000psi between or more) carry relatively low flow rate.According to a particular embodiment of the invention, guide piston 22 can be used to cam 17 to be positioned at complete travel position and complete in the arbitrary position between travel position.Therefore it is all obtainable, making the substantially maximized all flow rates of horsepower and the relevant pressure of pump 10.In other words, pump 10 for the motion with minute quantity parts move infinitely can positioning pressure compensated pump.

According to a particular embodiment of the invention, around each piston 30 of pre-eccentric device 44 location shown in Fig. 2, there is the corresponding resurrection plug (sister piston) 30 about rear eccentric 45 location around the longitudinal axis A of pump shaft 14.Yet other shapes in the present invention also may and can expect.For example, according to the embodiments of the invention that comprise 5 pistons 30,5 pistons can be made planetary or pentagon shape (that is, piston can mutually setover 72 degree).

According to a particular embodiment of the invention, the resultant vector of the piston group in each eccentric 44,45 and the resultant vector of the piston group in another eccentric 44,45 have the phase difference of 180 °.Described feature has prevented that the eccentric 44,45 shown in Fig. 2 from reversing cam 17 and therefore at least substantially having eliminated the needs that equilibrium block is set in pump 10.And described operation method has reduced whole cost and the complexity of pump 10.

Although only illustrate two eccentrics 44,45 in Fig. 2, according to another embodiment of the present invention, can utilize three or more eccentrics.For example, when when pump 10 comprises 3 eccentrics, each piston has the longitudinal axis A that two resurrections are filled in and each resurrection is filled in about pump shaft 14 in phase moving with piston 30 and setovers 120 °.Similarly, for example, when comprising four eccentrics, each piston 30 has the resurrection plug of three homophases.Therefore, according to a particular embodiment of the invention, by first piston, be applied to the resurrection plug that the power on cam 17 substantially always setovered by one or more homophases and be applied to the equilibrium of forces on cam 17.

A kind of method of process pump is provided according to another embodiment of the present invention.According to embodiment described in some, pump (for example, the pump 10 of above-mentioned discussion) for example, is located to be moved at the first pressure level (, about 1000psi).For example, same pump also can for example, be located to be moved being selected as the first power output stage that power stage at least basic and driving pump motor is consistent (, according to a particular embodiment of the invention about 1.5 horsepowers).

Then, pump is transformed to the second pressure level by first pressure level at the place of operation.According to a particular embodiment of the invention, described the second pressure level is on according to the about 6000psi in other embodiments of other embodiments or approximately on 10000psi or even higher.

In the operating pressure level of pump, from the first pressure level to the second pressure level during the conversion of (or even to other grades), specific embodiment of the present invention keeps the first power output stage substantially.Carry out and keep an exemplary method of the first power output stage to comprise that permission guide piston 22 is along with the pressure of pump raises and reduces and move along longitudinal axis A.According to described embodiment, cam 17 is moved to a plurality of positions along longitudinal axis A by guide piston 22.

As mentioned above, according to a particular embodiment of the invention, spring assembly 16 and guide piston 22 are specifically designed to variation moving ball 28A, 28B, 28C, the 28D in the groove 26 of the cam 17 shown in Fig. 1 along with the operating pressure of pump 10.More specifically, ball 28A, 28B, 28C, 28D are moved in groove 26, so that along with ball 28A, 28B, 28C, 28D are around longitudinal axis A rotation, piston 30 will be moved the distance of the rated power output stage that can keep pump 10.Therefore, can utilize the parts shown in Fig. 1 to realize the first power output stage of above-mentioned basic maintenance pump.

Said method also can comprise the vibration that minimizes pump by balanced fluid displacement mechanism is set.According to a particular embodiment of the invention, described step can by make pump 10 as shown in Figure 2 piston 30 location bias and by making mutually out of phase to move piston 30 operations so that the power of each piston on cam 17 setovers to be implemented.

Fig. 6 illustrates according to the cross section of another embodiment's again of the present invention piston cartridge 60.Piston cartridge 60 is included in the above-mentioned piston 30 in pump chamber 62.Machine oil inlet opening 64 is positioned at top and the bottom of the cross section of the chuck 60 shown in Fig. 6.Entrance check ball (checkball) 66 and check ball guide 68 also illustrate and navigate to 64 the right, inlet opening in Fig. 6.Have in abutting connection with the machine oil delivery outlet 76 of the output check ball 74 of its location and be positioned at pump chamber 62 sides.Chuck 60 is also included within the piston reset spring 50 that extends between the buttress thread 48 in its outside and the one end in piston 30 and piston cartridge 60.

Piston cartridge 60 shown in Fig. 6 is self-contained pump element, and it not only can be used as and pump 10 combinations shown in Fig. 1, also can be used as being combined with other pump and equipment.To those skilled in the art, when implementing one or more embodiment of the present invention, use pump and the equipment of the other types of piston cartridge 60 will become clear.

As shown in Figure 6, piston 30 is positioned piston cartridge 60 center.More specifically, piston 30 is arranged in pump chamber 62 and plays a part the pump piston at pump 10 pumping machine oil.As mentioned above, piston 30 is along with it is with one or more contacting in the eccentric shown in Fig. 1-4 and move.Yet traditional (that is, fixed displacement) camshaft or other elements also can be used to mobile piston 30.

Along with the piston 30 shown in Fig. 6 moves to right, the suction that suction check ball 66 produces by the motion by piston 30 is drawn towards piston 30.Piston 30 is also drawn into machine oil in pump chamber 62 by inlet opening 64 around suction check ball 66.Because output check ball 74 is tracted inwards by piston suction and is maintained on appropriate location by the C shape spring 78 (shown in Fig. 7) towards pedestal bias voltage, therefore when machine oil is inhaled in pump chamber 62 as mentioned above, the output check ball 74 shown in Fig. 6 prevents that machine oil from flowing through delivery outlet 76.

What abut against check ball 66 the right is check ball guide 68, and described check ball guide 68 is held check ball 66 and can be made by any material, but it is made of plastics conventionally.Ball guide portion 68 comprises the lug boss 70 of heart guiding check ball 66 in a plurality of relative check ball guide 68.Ball guide portion 68 also comprises that a plurality of permission machine oil is sent to the groove 72 pump chamber 62 from inlet opening 64.

As shown in Figure 6, in piston cartridge 60, also comprise the spring 73 being positioned between check ball 66 and check ball guide 68.Described spring 73 is 64 bias voltage check balls 66 towards inlet opening, and when piston 30 does not produce suction pressure, check ball 66 is located near inlet opening 64 and prevented that machine oil from flowing through.

When piston 30 moves to the left side of Fig. 6, inlet opening 64 is sealed by suction check ball 66 at least substantially.Equally, output check ball 74 is pushed open from piston 30 and is promoted machine oil by being positioned at the delivery outlet 76 of pump chamber 62 sides.

Fig. 7 is the panorama of the piston cartridge 60 shown in Fig. 6.As shown in Figure 7, low-pressure oil output groove 92 imports to inlet opening 64 by fluid.Equally, the high-pressure oil output groove 80 that C shape spring 78 is holding on the outside of piston cartridge 60 twines and crosses delivery outlet 76 extensions.Therefore,, when piston 30 moves to the right of Fig. 6, C shape spring 78 prevents from exporting check ball 74 and leaves chuck 60 completely.It should be noted, according to a particular embodiment of the invention, protuberance or other projections 57 are positioned on the internal surface of C shape spring 78.Described protruding 57 are typically inserted in the maintenance notch 59 being formed in high-pressure oil output groove 80, and prevent that C shape spring 78 from rotating around chuck 60.

In addition shown in Fig. 7, be threaded portion 82, thereby it typically comprise the screw thread (for example, the buttress thread shown in Fig. 6 48) that allows chuck 60 to be screwed to the position of fixed chuck 60 on pump or other equipment.Certainly, also can use other connecting method (for example, connecting assembling).In Fig. 7, illustrate aforesaid piston reset spring 50 and described piston reset spring 50 pushing piston 30.When there is no the reaction of other power, described spring 50 is returned to piston 30 position of Fig. 7 right-hand side.In addition the low pressure O shape circle 88 that, illustrates a pair of high pressure O-ring seals 86 and separate in Fig. 7.Pair of O shape circle sealing 86 is designed to prevent the oil leakage of chuck 60.

Fig. 8 illustrates the transparent perspective view of the pump circle subassembly 25 shown in Fig. 2, the lubricated chuck 61 that it comprises three chucks 60 shown in unique such as Fig. 7 and holds above-mentioned lube pistons 31.Circle subassembly 25 also illustrates and allows bolt to insert circle subassembly 25 to be connected to the bolt hole 63 on the miscellaneous part of said pump 10 by circle subassembly 25.

When machine oil is pumped out chuck 60, machine oil flows into high-pressure oil output groove 80.Equally, it should be noted, have the low pressure input oil passageway 96 shown in Fig. 8, it allows machine oil from oil tank 32 (shown in Fig. 1), to advance to the input groove 92 of chuck.

Fig. 9 illustrates another transparent perspective view of the pump circle subassembly 25 shown in Fig. 8.After machine oil flows into the high-pressure oil output groove 80 shown in Fig. 8, machine oil typically flows through in the delivery outlet passage 94 shown in Fig. 8 one and flow out towards the pump delivery outlet 40 (seeing Fig. 9) of pump 10.Described machine oil typically flows through in the channel 81 shown in Fig. 9.Figure 10 illustrates the stereogram of the exemplary apparatus of the pump 10 shown in Fig. 1.

An advantage of specific embodiment of the present invention is that above-mentioned geometrical shape has minimized the dead volume amount in pump chamber 62 when piston 30 is during in complete stroke.In other words, because machine oil is compressible to a certain extent, so the size of pump chamber 62 is minimized and exists current a small amount of machine oil to be compressed so that the fact of the maximizing efficiency of pump 10.Keep the end stroke of two less and close pistons 30 of delivery outlet 40 that dead volume is minimized.

Yet another advantage of specific embodiment of the present invention and the characteristic threads of chuck 60 make the chuck 60 can be relevant from pump 10 fact convenient and that fully detachably get off.Because can be designed as, check ball guide 68 can (for example easily disassemble from chuck 60, only by the one or more protuberances that unclamp), guide portion 68 cost maintenance or replaced and don't the pump that can interrupt within any prolongation endurance uses by another guide portion effectively.

According to another embodiment of the present invention, for example, provide the method for the piston of a kind of operation such as piston cartridge 60.Described method comprises hydraulic fluid (for example machine oil) is for example incorporated into, in piston chamber (, pump chamber 62).Described method also comprise utilize piston by masterpiece the hydraulic fluid for described chamber.For example, thus described step can pressure-acting be implemented to the machine oil in pump chamber 62 by the piston in Fig. 6 30 is moved to left.

Apart from the above, described method also comprises that for example, wherein, when piston is used for hydraulic fluid by masterpiece, at least one in outlet keeps substantially opening by piston from a plurality of outlets (, mouth 76) release hydraulic fluid.In other words, when utilizing chuck 60 to implement described step, at run duration, the stroke of piston 30 does not have total blockage outlet 76.

According to a particular embodiment of the invention, described method for example also comprises, when piston utilizes movable obstruction (, output check ball 74) when outlet is removed and substantially seals an outlet in a plurality of outlets.Described method also comprises utilizes retainer (for example, C shape spring 78) substantially around piston chamber.Then, described method can comprise and utilizes retainer to prevent that movable obstruction from departing from completely from piston cartridge.In other words, when piston 30 moves to the left side of Fig. 6, C shape spring 78 can be used as preventing from exporting check ball 74 and leave chuck.

Described method also comprises the housing that comprises as the device of piston chamber (in Fig. 6 as 98 illustrated in).Described method also comprises and is arranged on screw section on housing (for example, screw section 82), thereby is convenient to housing to disassemble from pump.In other words, because screw thread, the housing 98 of chuck 60 can be backed out and be replaced by new chuck 60.

The above pump 10 and chuck 60 can be implemented in many ways.For example, Fig. 9 illustrates the stereogram of the exemplary apparatus of said pump 10.Then Figure 10 illustrates another stereogram of the piston cartridge 60 shown in Fig. 6 and 7.Finally, Figure 11 illustrates another transparent perspective view of the pump circle subassembly 25 shown in Fig. 8.

Apart from the above, described method also comprises that allowing hydraulic fluid to pass through entrance (for example, mouth 64) enters chamber and basic sealed entry when piston moves towards entrance.Typically, this can utilize suction check ball 66 to realize.Further, described method can comprise the part constrained motion of the movable obstruction that utilizes the basic sealed entry of projection.Described step can utilize check ball guide 68 and the lug boss on it 70 to implement.Finally, described method can comprise the channel in the movable obstruction that allows hydraulic fluid to flow through basic sealed entry.Described step can utilize above-mentioned groove 80 to implement.

From detailed explanation, many feature and advantage of the present invention are significantly, and therefore intention is covered and fallen into the of the present invention all feature and advantage in actual aim of the present invention and scope by the claim of enclosing.Further, because numerous modifications and variations those skilled in the art will find apparent that, therefore do not require illustrated in limiting the invention to and accurate structure and the operation described, and correspondingly, all suitable modifications and equivalent can be resorted to and be fallen within the scope of the present invention.

Claims (14)

1. a pump, comprising:

Piston, it is removable along the first axle;

Eccentric cam, it is located about the second axle, and wherein said the second axle is basically perpendicular to described the first axle, and wherein said eccentric cam comprises level and smooth non-linear groove;

Final controlling element, its contiguous described cam orientation is also configured to make described cam to move along described the second axle;

The first nearly camshaft bearing, during it is positioned at non-linear groove between described piston and described cam and be configured so that cam causes that along the change in location of described the second axle described bearing is along the change in location of described the first axle, wherein when described cam moves along described the second axle described in the first nearly camshaft bearing keep substantially along described the first axle location; And

Thrust bearing assembly, the torque arm that it is arranged on the described eccentric cam of described pump and minimizes pump between the described final controlling element of position that regulates described eccentric cam during described pump operation.

2. pump according to claim 1, wherein said final controlling element comprises spring assembly.

3. pump according to claim 2, wherein said spring assembly comprises first spring with the first spring constant and second spring with the second spring constant.

4. pump according to claim 3, wherein said the first spring constant and described the second spring constant are unequal.

5. pump according to claim 1, wherein said final controlling element comprises:

Pin, it is configured to exert pressure along described the second axial described cam; And

Nearly pin bearing, it is positioned between described pin and described cam.

6. pump according to claim 1, further comprises:

Camshaft, it is substantially around a part for described cam and a part for described final controlling element.

7. pump according to claim 6, further comprises:

Nearly camshaft bearing, it is substantially around described camshaft.

8. pump according to claim 1, wherein said eccentric cam comprises and is formed on its outside groove, and the wherein said first nearly camshaft bearing is positioned in described groove.

9. pump according to claim 1, further comprises:

The second nearly camshaft bearing, it is setovered and is positioned from the described first nearly camshaft bearing about described cam, so that when described cam rotates about described the second axle, 180 ° of the described first nearly camshaft bearing and the mutual out-of-phase motions of the described second nearly camshaft bearing.

10. pump according to claim 9, further comprises:

The 3rd nearly camshaft bearing, about described cam, from the described first nearly camshaft bearing and the described second nearly camshaft bearing, the two is all setovered and is further positioned for it, so that when described cam rotates about described the second axle, the described first nearly camshaft bearing, the described second nearly camshaft bearing and the mutual out-of-phase motion of the described the 3rd nearly camshaft bearing are with pump described in balance.

11. pumps according to claim 1, further comprise:

Bearing guide portion, it is located and is configured to make the described first nearly camshaft bearing to minimize with respect to the transverse movement of described piston in abutting connection with the described first nearly camshaft bearing.

12. pumps according to claim 1, further comprise:

Lube pistons, the path that it is close to described cam orientation and is configured to be provided to Lubricants described cam.

13. pumps according to claim 12, further comprise:

The second nearly camshaft bearing, it is positioned between described lube pistons and described cam, and wherein, when described cam moves along described the second axle, the described second nearly camshaft bearing keeps substantially along described the first axle location.

14. 1 kinds of pumps, comprising:

Translating device, it is for along the first axle translation;

Slewing gear, it is for rotating about the second axle, and wherein said the second axle is basically perpendicular to described the first axle, and wherein said slewing gear comprises level and smooth non-linear groove;

Actuating device, it is for making described slewing gear move along described the second axle;

Tourelle, it rolls for the outer surface around described slewing gear, and it is in described non-linear groove and be configured such that described slewing gear causes that along the change in location of the second axle of described slewing gear described tourelle is along the change in location of described the first axle, wherein said tourelle is positioned between described translating device and described slewing gear, and wherein, when described slewing gear moves along described the second axle, described tourelle keeps substantially along described the first axle location; And

Thrust bearing assembly, the torque arm that it is arranged on the described slewing gear of described pump and minimizes pump between the described actuating device of position that regulates described slewing gear during described pump operation.