CN101517234A - Piston cartridge - Google Patents

Abstract

A piston cartridge has a piston chamber, an inlet port, an outlet port, and a piston moveable between a first position and a second position. Also, the cartridge includes a first barrier positioned between the piston and the inlet port and a first sealing member moveable between the first barrier and the inlet port, wherein the first sealing member seals the inlet port when positioned adjacent to the inlet port but allows the fluid into the chamber when positioned adjacent to the first barrier. In addition, the cartridge also includes a second barrier positioned adjacent to the outlet port and a second sealing member moveable between the piston and the second barrier, wherein the second sealing member seals the outlet port when positioned adjacent thereto but allows the fluid to pass through the outlet port when positioned adjacent to the second barrier.

Description

Piston cartridge

The cross reference of related application

[0001] the application requires to be called the interests that pressure compensated pump, application number are 60/843,701 U.S. Provisional Patent Application in the name of submitting to for 2006 09 month No. 12, thus its full content is incorporated herein by reference.

Technical field

[0002] the present invention relates generally to oil hydraulic pump.More particularly, when fluctuation takes place the pressure of their operations place, can still enough keep the pump of constant horsepower output even the present invention relates to.

Background technique

[0003] be obtainable even when fluctuation takes place the pressure of their operations place, still can keep the pump of constant horsepower output current.These pumps are designed to, and utilize the shaft horsepower amount maximization that is input to a certain amount of horsepower of pump by motor usually and makes described pump, and no matter the pressure of their operations place.Therefore, these pumps and other pumps that can not keep constant horsepower output mutually specific energy more effectively move.

[0004] typically, can keep the pump of constant horsepower output in low relatively pressure range, to move.On the other hand, the pump that moves in higher pressure range can not keep constant horsepower output along with the variation of the operating pressure of pump.Typically, described high-pressure service pump is that a plurality of pumps that multistage pump and the main mechanism that is changed between a plurality of pumps by utilization link together are formed.

[0005] therefore, even the pump with novelty and the method that under high pressure still can keep constant horsepower output need be provided.Also need to provide the pump of forming by infinite stages (that is, its actual be single-stage pump (singlepumps)) with novelty.

[0006] except that above-mentioned, thereby also needs to provide the pump that modularization is keeped in repair easily and maintenance cost is low.Further, need provide by the total measurement (volume) that is included in piston chamber wherein being minimized make the pump of its maximizing efficiency.

Summary of the invention

[0007] by providing a kind of piston cartridge can satisfy above-mentioned requirements largely in one embodiment of the invention.Described piston cartridge comprises piston chamber.Described piston cartridge also comprises inlet, and its adjacent piston chamber is located and provided fluid can enter the path of piston chamber by it.Described piston cartridge further comprises first outlet, and its adjacent piston chamber is located and provided fluid can leave the path of piston chamber by it.In addition, described piston cartridge also comprises and being positioned at least in part in the piston chamber and in piston mobile near the primary importance of inlet and between relatively away from the second place of inlet relatively.Equally, described piston cartridge comprises first dividing plate that is positioned between piston and the inlet.Further, described piston cartridge comprises and is positioned between first dividing plate and the inlet and first sealed member movably between first dividing plate and inlet, wherein when the first sealed member neighboring entry is located, its basic sealed entry, and when contiguous first dividing plate of first sealed member location, it allows fluid to flow into piston chamber.In addition, piston cartridge also comprises the second partition of the contiguous first outlet location.Described piston cartridge also comprises and is positioned between piston and the second partition and second sealed member movably between piston and second partition, wherein when contiguous first outlet of second sealed member is located, it seals first outlet substantially, and when the contiguous second partition of second sealed member location, it allows fluid to flow through first outlet.

[0008] according to another embodiment of the present invention, provide a kind of method of moving piston.It is relative to the second place that enters the mouth that described method comprises that the primary importance that the piston in the piston chamber is entered the mouth from close relatively piston chamber moves to.Described method be also included within when allowing to be configured to the neighboring entry location that first sealed member of sealed entry leaves inlet and with piston when primary importance moves to the second place, allow fluid to flow into piston chamber.Thereby described method further be included in by allow second sealed member towards outlet move form with it sealing with piston when primary importance moves to the second place, prevent that fluid from flowing out from piston chamber.

[0009] according to another embodiment again of the present invention, provides another piston cartridge.Described piston cartridge comprises the fluid containment device that holds fluid and fluid introduced the fluid leading device of fluid containment device, wherein fluid leading device adjacent fluid receiving means location and provide fluid to enter the path of fluid containment device by it.Described piston cartridge also comprises and being used for fluid from fluid containment device fluid ejector of drawing and the fluid displacement apparatus that is used to fluid is moved, fluid ejector adjacent fluid receiving means location and provide fluid to leave the path of fluid containment device wherein by it, and wherein fluid displacement apparatus to small part is positioned in the fluid containment device and relatively near the primary importance of fluid leading device and removable between the second place away from the fluid leading device relatively.In addition, piston cartridge also comprises first seal arrangement that is used to provide first baffle plate device of first dividing plate and is used to provide the first fluid sealing, described first baffle plate device is positioned between fluid displacement apparatus and the fluid leading device, described first seal arrangement is positioned between first baffle plate device and the fluid leading device and is removable between first baffle plate device and fluid leading device, wherein when the first seal arrangement adjacent fluid leading device is located, its fluid-encapsulated substantially leading device, and when the contiguous the～baffle plate device of first seal arrangement location, it allows fluid to flow in the fluid containment device.Piston cartridge also comprises the second partition device and second seal arrangement that is used to provide second partition, described second partition device adjacent fluid ejector location, and described second seal arrangement is positioned between fluid displacement apparatus and the second partition device and removable between fluid displacement apparatus and second partition device, wherein when the second seal arrangement adjacent fluid ejector is located, its fluid-encapsulated substantially ejector, and when the contiguous second partition device of second seal arrangement location, it allows fluid to pass the fluid ejector.

[0010] still according to another embodiment of the present invention, provide the other method of process pump.Described method comprises makes eccentric shape cam ring around first rotation.Described method also comprises makes cam along first translation.Described method further comprise along with cam along first translation and along first holding position of the bearing of contiguous cam.In addition, described method comprises that also the piston and the bearing that will be close to the bearing location when cam rotation promote together.Described method further comprises the substantially invariable power output level that keeps coming self-pumping when cam during along first translation.

[0011], and, summarized specific embodiment of the present invention quite widely in order to estimate reality contribution better to prior art in order to understand detailed description of the present invention better.Certainly, additional embodiments of the present invention will be described below and form the theme of the claim that is additional to this.

[0012] in described scheme, before describing at least one embodiment of the present invention in detail, it should be understood that the present invention in it is used, be not limited to set forth in the following description or accompanying drawing in illustrated CONSTRUCTED SPECIFICATION and member configuration.Except the embodiment who describes, puts into practice and carry out in every way, the present invention can instantiation.It should be understood that equally word, term and summary all are for purpose of description as used herein, and should not be considered to restriction.

[0013] therefore, what it should be appreciated by those skilled in the art is, described open institute based on design can be easily as the basis of designing other structures, and the method and system that is used to carry out several purposes of the present invention.Therefore, importantly, the claim that is believed to comprise described equivalent structure is in the scope that does not break away from aim of the present invention and scope.

Description of drawings

[0014] Fig. 1 illustrates the cross section according to the pump of the first embodiment of the present invention.

[0015] Fig. 2 illustrates the stereogram of cross section of the inside of pump shown in Figure 1.

[0016] Fig. 3 illustrates the part of the cross section of pump shown in Figure 1, and wherein camshaft is in complete travel position.

[0017] Fig. 4 illustrates the part of the cross section of pump shown in Figure 1, and wherein camshaft is in does not have stroke (destroked) position fully.

[0018] Fig. 5 illustrates three typical horsepower curves of the pump shown in Fig. 1 to 4.

[0019] Fig. 6 illustrates the cross section according to another embodiment's again of the present invention piston cartridge.

[0020] Fig. 7 is the panorama of piston cartridge shown in Figure 6.

[0021] Fig. 8 illustrates the transparent perspective view of the pump circle subassembly shown in Figure 2 that comprises three chucks and a lubricated chuck.

[0022] Fig. 9 illustrates another transparent perspective view of pump circle subassembly shown in Figure 8.

[0023] Figure 10 illustrates the stereogram of the typical equipments of pump shown in Figure 1.

Embodiment

[0024] describe the present invention below in conjunction with accompanying drawing, wherein identical reference character is represented identical parts all the time.Fig. 1 illustrates the cross section according to 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 first end with contiguous motor 12 and the spring assembly 16 that is close to the second end of cam 17.

[0025] according to a particular embodiment of the invention, spring assembly 16 comprises the group cover (stack) of two, three or more springs.When using three springs, hard spring (that is, have high elastic constants and can produce the spring of big elastic force when being compressed) typically is positioned at the right of more close spring assembly 16 shown in Figure 1 and locates.Then, medium spring is positioned at the centre of spring assembly 16, and soft spring is positioned near the cam 17.Three kinds of springs form progressive spring assembly 16 together, and described spring assembly 16 is with other member positioning cams 17 that are used to respect to pump 10 as described below.According to a particular embodiment of the invention, each spring of a plurality of springs in the spring assembly 16 has different spring rate/elastic force.Yet, have two of identical springs rigidity/elastic force also within the scope of the invention with the structure of upper spring.

[0026] in Fig. 1, spring assembly 16 is about contained spring guide rod 13 location.Contained spring guide rod 13 is positioned at inside, the adjacent pins 11 of axle 14 concentrically and keeps spring assembly 16 to be in the center of axle 14 substantially.Be positioned at the most close cam 17 spring assembly 16 end place be cam sealing plug 15, described cam sealing plug 15 is designed to, and prevents that the liquid of just lubricated cam 17 is leaked on the spring assembly 16.

[0027] be in operation, motor 12 is mechanically connected to pump shaft 14 and cam 17 and makes the both rotate.According to a particular embodiment of the invention, cam 17 with about 3000 and approximately the rpm between the 4000rpm rotate.Yet other rpm scope also within the scope of the invention.

[0028] as shown in Figure 1, pump shaft 14 is by pair of bearings 18 supportings.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, other members that described axle saddle 24 is generally used for keeping pump 10 in position, this will be by becoming clear with reference to the accompanying drawings.

[0029] be close to cam 17 end location be guide piston 22, described cam 17 and spring assembly 16 relative positionings, described guide piston 22 are effectively as the final controlling element along the longitudinal axis A wedge cam 17 of pump shaft 14.According to a particular embodiment of the invention, spherical substantially object (for example ball) or all as shown in Figure 1 thrust bearing assemblies of element 23 are positioned between guide piston 22 and the cam 17 to promote the axial rotation of cam 17 with respect to guide piston 22.Substantially spherical object or thrust bearing assembly 23 typically can rotate along with the rotation of cam 17.

[0030] according to other specific embodiments of the present invention, guide piston 22 is along the longitudinal axis A extension of pump shaft 14 and arrives against the little bar of the point of cam 17 location.According to described embodiment, guide piston 22 provides single-point contact and so the uncorrelated torque arm against cam 17.Therefore, cam 17 can not need rotary seal with high relatively rpm rotation.To replacing the situation of the embodiments of the invention of single-point contact with thrust bearing assembly 23 or spherical substantially object also is the same.

[0031] cam 17 has a plurality of grooves 26 that are formed on wherein, and as shown in Figure 1, described cam 17 is a combination saw dentation and typically about the longitudinal axis A off-centre of cam (described longitudinal axis A also is the longitudinal axis of the pump shaft 14 among Fig. 1).That is held in each of groove shown in Figure 1 26 is ball 28A, 28B, 28C, 28D.Ball 28A, 28B shown in Figure 1, each among 28C, the 28D all be positioned between piston 30 and the lube pistons 31 and with the central shaft of piston 30,31 on 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 liquid displacement 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 race ring shown in Figure 2 44 and 45 around the longitudinal axis A of pump shaft 14, and they combine as eccentric.

[0032] in Fig. 1, the mutual vertical arrangement of ball 28A and 28B is in line and forms first pair of ball, and the also mutual vertical array of ball 28C and 28D is in line and forms second pair of ball.The every pair of ball also with piston 30 shown in Figure 1 in one and lube pistons 31 in one vertically be arranged in a straight line.In every pair of ball, the relative longitudinal axis A location of a ball (for example, 28A and 28D) near pump shaft 14, and another ball in a pair of ball (for example, 28B and 28C) 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 constituted eccentric, and each among ball 28A, 28B, 28C, the 28D all will influence the deviation post of the eccentric that contacts with lube pistons 31 with piston 30.

When [0033] in eccentric and piston 30 and lube pistons 31 contacts, relatively will outwards promote in eccentric and piston 30 or the lube pistons 31 one, and will allow another piston 30 and lube pistons 31 towards the inside rollback of longitudinal axis A near ball 28A, the 28D of longitudinal axis A relatively away from ball 28B, the 28C of the longitudinal axis A of pump shaft 14.Total distance that piston 30 was advanced when eccentric and cam 17 were finished a rotation (, piston stroke) and judge have how many fluids can flow through pump 10.Usually, the distance that piston 30 is advanced is long more, and the fluid that flows through pump 10 is many more.

[0034] pump 10 shown in Figure 1 also comprise oil tank 32 (that is oil storage tank), suction filter 34, return tube 36, from the input oil groove 38 of oil tank 32 and the pump delivery outlet 40 that flows that holds to come the high pressure oil of self-pumping 10.Be in operation, machine oil is from oil tank 32 flow through suction filter 34, the input oil groove of flowing through 38 and enter into piston chamber's (for example, shown in Figure 6 pump chamber 62) of contiguous piston 30 shown in Figure 1.Piston 30 acts on pressure machine oil in the piston chamber and passes through pump delivery outlet 40 and discharges machine oil then.Yet other pump structure also within the scope of the invention.

[0035] Fig. 2 illustrates the stereogram of cross section of the inside of pump shown in Figure 1 10.Cross section shown in Figure 2 is perpendicular to cross section shown in Figure 1.The front of Fig. 2 is also consistent with the cross section of pump circle subassembly 25.As shown in Figure 2, in contiguous axle saddle 24 of two ball 28A, 28B of the either side of cam 17 and race ring 42 location.The outside of race ring 42 is close in two eccentrics 44,45 shown in Figure 2.Pre-eccentric device 44 is illustrated as the most proximal end that is positioned at cross section, and then eccentric 45 is positioned at the back (that is more close motor 12) of pre-eccentric device 44.

[0036] as will be explained hereinafter, pump 10 is a pressure compensated pump, when cam 17 is suitably located with respect to pump shaft 14 and piston 30, pump 10 can carry the function that is moved as pump 10 variation fluid flow and carried the fluid flow that changes with pump 10 by any pressure of operation place.According to certain embodiments of the present invention, and as hereinafter described, pump 10 is configured to, the pressure by monitoring pump operation place and by utilizing himself operation of force value control to come himself output performance of optimization.

[0037] by limiting, in order to judge the horsepower of pump, at first make from the fluid flow (for example, gpm) of pump outflow and the pressure of pump operation place and multiply each other, make the value that calculates divided by a constant then.For example, when utilizing 1.5 horsepowers motor as motor 12 driven pumps 10, typical preferred is, with near rated horsepower level run pump to optimize its performance.Same typical preferred be, even when the operating pressure of pump fluctuates, still can keep pump with level run near rated horsepower.

[0038] present, need a kind of like this pump on the market: even when the pressure surge at pump operation place, described pump also can keep reaching 10000psi scope and above constant horsepower output (that is the pressure compensated pump that need move with high relatively pressure).Yet present obtainable pressure compensated pump preferably also can only move in reaching 2000 to 5000psi scope.Equally, even at these relatively low pressure places, current available pressure compensated pump also is complicated, expensive and heavy mechanism.

[0039] the available pump that moves in the 10000+psi scope at present is a multistage pump, and therefore can not provide continuous pressure compensation.Definitely, whenever impelling, the operating pressure of the rising of pump transforms or when transitting to a new stage, 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 following descending mechanism (step-down mechanism) that comprises in complexity, costliness and the heavy this pump is each stage motion striking plate and/or valve plate or non-loaded valve.

[0040] 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 simple relatively that the member of pump 10 is designed to be, and with as described below, the operation of pump 10 is effective relatively.

[0041] Fig. 3 illustrates the part of the cross section of pump shown in Figure 1 10, 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 the part of the cross section of pump shown in Figure 1 10, and wherein camshaft 17 is in does not have travel position fully (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.

[0042] when implementing embodiments of the invention, what it should be appreciated by those skilled in the art is, when cam 17 was located as shown in Figure 3 and rotated by motor 12 (shown in Figure 1), the maximum stroke that piston 30 experience are allowed by pump 10 also provided maximum flow to keep given horsepower.On the other hand, when cam 17 was located as shown in Figure 4, piston 30 experienced the stroke of the minimum degree that still allows pump 10 as plan to be moved.The position adjustment of following cam 17 will allow pump 10 to provide needed maximum horsepower at the operating pressure place of pump 10.

[0043] Fig. 5 illustrates three representational horsepower curves.Solid line is based on theoretical horsepower data, and two dotted lines are based on the survey data less than two typical two stage pumps that advance along horsepower curve.According to a particular embodiment of the invention, the profile of cam 17 (profile) (promptly, the curvature of groove 26) (promptly with the design of spring assembly 16, be included in the relative force that the spring in the spring assembly 16 is applied when pressurized) and the relation of guide piston power is together, and pump 10 is kept along indicated horse power curve motion shown in Figure 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 exponential function and utilizes hundreds of the data points of being taked under the different flow volume of maximized different operating pressure of the horsepower output that makes pump 10 and pump 10 to produce.

[0044] according to a particular embodiment of the invention, horsepower curve is level and smooth so that continuously.This considers that the groove 26 in the cam also is level and smooth and continuous.When pump 10 operations, guide piston 22 applies power on cam 17, and described power typically equals the pressure of pump 10 operations place own or is the function of the pressure of pump 10 operations place own.According to a particular embodiment of the invention, closed feedback loop signal is used to control guide piston 22 (following discussion).According to another embodiment of the invention, can provide manual or automatic joining portion with control guide piston 22.Equally, those skilled in the art implement to become when of the present invention control guide piston 22 clearly other devices also within the scope of the invention.

[0045] anyway control, the power that directly or indirectly is applied on the cam 17 by guide piston 22 is positioned at the optimal substantially position of operating pressure that relative piston 30 is in pump 10 with cam 17.In other words, cam 17 is positioned so that ball 28A, 28B, 28C, 28D impel the stroke distances of piston 30 to the flow rate that is provided for pump 10, the described basic optimization of flow rate that is used for pump 10 rated horsepower of pump 10 at its operating pressure place.

[0046] turn back to the discussion of Fig. 3 and 4, in complete travel position shown in Figure 3, pump 10 is carried high relatively flow rate with low relatively pressure (for example, only a small amount of psi).Do not have travel position fully shown in Figure 4, pump with high relatively pressure (for example, 6000 and 10000psi between or more) carry low relatively flow rate.According to a particular embodiment of the invention, guide piston 22 can be used to that cam 17 is positioned at complete travel position and not have any position between the travel position fully.Therefore, maximize substantially pump 10 horsepower all flow rates be obtainable with relevant pressure.In other words, but the unlimited positioning pressure compensated pump that pump 10 moves for the motion with the minute quantity member.

[0047] according to a particular embodiment of the invention, has the corresponding resurrection plug (sister piston) 30 about eccentric 45 location, back around each piston 30 of pre-eccentric device shown in Figure 2 44 location around the longitudinal axis A of pump shaft 14.Yet other shapes in the present invention also may and can reckon with.For example, according to the embodiments of the invention that comprise 5 pistons 30,5 pistons can make starlike or pentagon shape (that is, piston can setover mutually 72 degree).

[0048] according to a particular embodiment of the invention, the resultant vector of the resultant vector of the piston set in each eccentric 44,45 and the piston set in another eccentric 44,45 has 180 ° phase difference.Described feature has prevented that eccentric shown in Figure 2 44,45 from reversing cam 17 and therefore eliminated the needs that equilibrium block is set at least basically in pump 10.And described operation method has reduced the whole cost and the complexity of pump 10.

[0049] although in Fig. 2, only illustrate two eccentrics 44,45, according to another embodiment of the present invention, can utilize three or more eccentrics.For example, when comprising 3 eccentrics in pump 10, each piston has the longitudinal axis A that two resurrections are filled in and each resurrection is filled in about pump shaft 14 that in phase moves 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, the power that is applied on the cam 17 by first piston substantially always is applied to equilibrium of forces on the cam 17 by the resurrection plug of one or more homophases biasing.

A kind of method of process pump is provided [0050] according to another embodiment of the present invention.According to some described embodiments, pump (for example, the pump 10 of above-mentioned discussion) is located to be moved at first stress level (for example, about 1000psi).For example, same pump also can be located to be moved being selected as first basic consistent with the power of electric motor level of the driven pump at least power output level (for example, according to a particular embodiment of the invention about 1.5 horsepowers).

[0051] then, pump is transformed to second stress level by first stress level at the place of operation.According to a particular embodiment of the invention, described second stress level is on about 6000psi or approximately on the 10000psi or even higher in other embodiments according to other embodiments.

[0052] the operating pressure level of pump from first stress level during the conversion of second stress level (perhaps even to other levels), specific embodiment of the present invention keeps the first power output level substantially.Carry out an exemplary method that keeps the first power output level and comprise that permission guide piston 22 is along with the pressure rising and the reduction of pump are moved 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.

[0053] as mentioned above, according to a particular embodiment of the invention, spring assembly 16 and guide piston 22 are specifically designed to variation mobile ball 28A, 28B, 28C, the 28D in the groove 26 of cam shown in Figure 1 17 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 rotate around longitudinal axis A, piston 30 will be moved the distance of the rated power output level that can keep pump 10.Therefore, can utilize member shown in Figure 1 to realize the first power output level of above-mentioned basic maintenance pump.

[0054] method of above-mentioned discussion also can comprise by the vibration that equilibrium flow displacement body mechanism minimizes pump is set.According to a particular embodiment of the invention, the location bias of the piston 30 that described step can be by making pump 10 as shown in Figure 2 and by making mutually piston 30 operations out of phase so that the power of each piston on the cam 17 is setovered is implemented.

[0055] Fig. 6 illustrates the cross section according to another embodiment's again of the present invention piston cartridge 60.Piston cartridge 60 is included in the above-mentioned piston 30 in the pump chamber 62.Machine oil inlet opening 64 is positioned at the top and the bottom of the cross section of chuck shown in Figure 6 60.Inlet check ball (checkball) 66 and check ball guide 68 also illustrate and navigate to 64 the right, inlet opening in Fig. 6.Machine oil delivery outlet 76 with output check ball 74 of contiguous its location is 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 end in piston 30 and piston cartridge 60.

[0056] piston cartridge 60 shown in Figure 6 is the self-contained pump element, and it not only can be used as with pump 10 shown in Figure 1 and combine, and also can be used as with other pump and equipment to combine.To those skilled in the art, when implementing one or more embodiment of the present invention, can use the pump and the equipment of the other types of piston cartridge 60 will become clear.

[0057] as shown in Figure 6, piston 30 is positioned the center of piston cartridge 60.More specifically, piston 30 is arranged in pump chamber 62 and plays a part pump piston at pump 10 pumping machine oil.As mentioned above, piston 30 along with its with the eccentric shown in Fig. 1-4 in one or more contacting and move.Yet traditional (that is fixed displacement) camshaft or other elements also can be used to mobile piston 30.

[0058] along with piston shown in Figure 6 30 moves to right, suction check ball 66 is drawn towards piston 30 by the suction that the motion by piston 30 produces.Piston 30 also is drawn into machine oil in the pump chamber 62 by inlet opening 64 around suction check ball 66.Because output check ball 74 is tracted inwards by piston suction and remains on the appropriate location by the C shape spring 78 (shown in Figure 7) towards the pedestal bias voltage, therefore when making machine oil be inhaled in the pump chamber 62 as mentioned above, output check ball 74 shown in Figure 6 prevents that machine oil from flowing through delivery outlet 76.

What [0059] 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 usually.Ball guide portion 68 comprises the lug boss 70 of a plurality of relative check ball guide 68 to center guiding check ball 66.Ball guide portion 68 comprises that also a plurality of permission machine oil are sent to the groove 72 the pump chamber 62 from inlet opening 64.

[0060] as shown in Figure 6, also comprise the spring 73 that is positioned between check ball 66 and the check ball guide 68 in the piston cartridge 60.Described spring 73 is 64 bias voltage check balls 66 towards the inlet opening, and when piston 30 did not produce suction pressure, check ball 66 nestled up 64 location, inlet opening and prevents that machine oil from flowing through.

[0061] 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.

[0062] Fig. 7 is the panorama of piston cartridge 60 shown in Figure 6.As shown in Figure 7, low-pressure oil input groove 92 imports to inlet opening 64 with fluid.Equally, C shape spring 78 is holding the high-pressure oil output groove 80 on the outside of piston cartridge 60 and is crossing delivery outlet 76 and extend.Therefore, when piston 30 moved to the right of Fig. 6, C shape spring 78 prevented to export check ball 74 and leaves chuck 60 fully.It should be noted that according to a particular embodiment of the invention, protuberance or other projectioies 57 are positioned on the internal surface of C shape spring 78.Described protruding 57 typically are inserted in the maintenance notch 59 that is formed in the high-pressure oil output groove 80, and prevent that C shape spring 78 from rotating around chuck 60.

[0063] in addition, be threaded portion 82 shown in Fig. 7, thereby it typically comprise the screw thread that allows chuck 60 to be screwed to the position of fixed chuck 60 on pump or other equipment (for example, shown in Figure 6 buttress thread 48).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 not having the reaction of other power, described spring 50 returns to piston 30 position of Fig. 7 right-hand side.In addition, the low pressure O shape circle 88 that in Fig. 7, illustrates a pair of high pressure 0 shape seal ring 86 and separate.A pair of 0 shape circle sealing 86 is designed to prevent the oil leakage of chuck 60.

[0064] Fig. 8 illustrates the transparent perspective view of pump circle subassembly 25 shown in Figure 2, and it comprises three such as the chuck shown in unique among Fig. 7 60 with hold a lubricated chuck 61 of above-mentioned lube pistons 31.Circle subassembly 25 also illustrates and allows bolt to insert will enclose the bolt hole 63 on other members that subassembly 25 is connected to said pump 10 by circle subassembly 25.

[0065] when machine oil is pumped out chuck 60, machine oil flows into high-pressure oil output groove 80.Equally, it should be noted that have low pressure input oil passageway 96 shown in Figure 8, it allows machine oil to advance to the input groove 92 of chuck from oil tank 32 (shown in Figure 1).

[0066] Fig. 9 illustrates another transparent perspective view of pump circle subassembly 25 shown in Figure 8.After machine oil flow into high-pressure oil shown in Figure 8 output groove 80, machine oil typically flow through in the delivery outlet passage 94 shown in Figure 8 one and flow out towards pump delivery outlet 40 (see figure 9)s of pump 10.Flowing of described machine oil typically by one in the channel 81 shown in Figure 9.Figure 10 illustrates the stereogram of typical case's enforcement of pump shown in Figure 1 10.

[0067] specific embodiment of the present invention advantage is when piston 30 is in complete stroke, and above-mentioned geometrical shape has minimized the dead volume amount in the pump chamber 62.In other words, because machine oil is compressible to a certain extent, so the size of pump chamber 62 is minimized and exist current a spot of machine oil to be compressed so that the fact of the maximizing efficiency of pump 10.Keep the end stroke of two delivery outlets, 40 less and close pistons 30 to minimize dead volume.

[0068] however another advantage of specific embodiment of the present invention and the characteristic threads of chuck 60 make chuck 60 convenient and the fully detachable following fact is relevant from pump 10.Because check ball guide 68 can be designed as and can (for example easily disassemble from chuck 60, one or more protuberances only), guide portion 68 cost maintenance or replace and don't the pump that can interrupt in any prolongation endurance uses effectively by another guide portion by unclamping.

[0069] 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 incorporated in the piston chamber (for example, pump chamber 62).Described method also comprises utilizes piston that masterpiece is used for hydraulic fluid.For example, thus described step can affact pressure on the machine oil in the pump chamber 62 by the piston among Fig. 6 30 is moved to left to be implemented.

[0070] except that above-mentioned, described method comprises that also wherein when piston was used for hydraulic fluid with masterpiece, at least one in the outlet kept open substantially by piston from a plurality of outlets (for example, 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.

[0071] according to a particular embodiment of the invention, described method also comprises when piston utilizes movable obstruction (for example, output check ball 74) when outlet is removed and seals an outlet in a plurality of outlets substantially.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 breaks away from from the piston cartridge fully.In other words, when piston 30 moved to the left side of Fig. 6, C shape spring 78 can be used as and prevents to export check ball 74 and leave chuck.

[0072] described method also comprises the housing that comprises as the parts of piston chamber (among Fig. 6 as 98 illustrated in).Described method also comprises and is arranged on screw section on the housing (for example, screw section 82), thereby is convenient to housing is disassembled 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.

[0073] 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.Figure 10 illustrates another stereogram of the piston cartridge 60 shown in Fig. 6 and 7 then.At last, Figure 11 illustrates another transparent perspective view of pump circle subassembly 25 shown in Figure 8.

[0074] except that above-mentioned, described method comprises that also the permission hydraulic fluid enters chamber and basic sealed entry when piston is mobile towards inlet by inlet (for example, mouth 64).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.At last, 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.

[0075] from detailed explanation, many feature and advantage of the present invention are significantly, and therefore intention covers all feature and advantage of the present invention in actual aim of the present invention and the scope by the claim of enclosing.Further, because numerous modifications and variations those skilled in the art will find apparent that, therefore illustrated in not wishing to limit the invention to and accurate structure and the operation described, and correspondingly, the modification that all are suitable and be equal to be resorted to and fall within the scope of the present invention.

Claims (20)

1, a kind of piston cartridge comprises:

Piston chamber;

Inlet, its contiguous described piston chamber location also provides fluid can enter the path of described piston chamber by it;

First outlet, its contiguous described piston chamber locatees and provides fluid can leave the path of described piston chamber by it;

Piston, it is positioned in the described piston chamber and at least in part relatively near the primary importance of described inlet and removable between the second place away from described inlet relatively;

First dividing plate, it is positioned between described piston and the described inlet;

First sealed member, it is positioned between described first dividing plate and the described inlet and is removable between described first dividing plate and described inlet, wherein when the contiguous described inlet of described first sealed member location, it seals described inlet substantially, and when contiguous described first dividing plate of described first sealed member location, it allows fluid to flow into piston chamber;

Second partition, its contiguous described first outlet location; And

Second sealed member, it is positioned between described piston and the described second partition and is removable between described piston and described second partition, wherein when contiguous described first outlet of described second sealed member is located, it seals described first outlet substantially, and when the contiguous described second partition of described second sealed member location, it allows fluid to flow through described first outlet.

2, piston cartridge according to claim 1, wherein said first sealed member comprises basic globular part.

3, piston cartridge according to claim 1, wherein said second partition is positioned at the outside of described piston chamber.

4, piston cartridge according to claim 1 further comprises:

Housing, it comprises described piston chamber; And

Screw section on the described housing, it is configured to allow described piston cartridge to be screwed on the pump.

5, piston cartridge according to claim 4 further comprises:

The groove of outside, described second partition is contained in the described groove.

6, piston cartridge according to claim 4 further comprises:

The groove of outside, its fluid that is configured to flow therein is directed to needed position.

7, piston cartridge according to claim 4, wherein said second partition comprise the C shape spring that is positioned at described outside.

8, piston cartridge according to claim 1 further comprises:

Second outlet, its contiguous described piston chamber locatees and provides another fluid can leave the path of described piston chamber by it; And

The 3rd sealed member, it is positioned between described piston and the described second partition and is removable between described piston and described second partition, wherein when contiguous described second outlet of described the 3rd sealed member is located, it seals described second outlet substantially, and when the contiguous described second partition of described the 3rd sealed member location, it allows fluid to flow through described second outlet.

9, piston cartridge according to claim 1 further comprises the spring that restoring force is acted on described piston when described piston is in position except the second place.

10, a kind of method of moving spring, described method comprises:

Piston in the piston chamber is moved to the relative second place away from described inlet from the primary importance that enters the mouth near piston chamber relatively;

First sealed member that seals described inlet when allowing to be configured to contiguous described inlet location leave described inlet and with described piston when described primary importance moves to the described second place, allow fluid to flow into described piston chamber;

Thereby by allow second sealed member towards outlet move form with it sealing with described piston when described primary importance moves to the described second place, prevent that fluid from flowing out from described piston chamber.

11, method according to claim 10 further comprises:

Described piston is moved to described primary importance from the described second place;

When make described piston when the described second place moves to described primary importance by described first sealed member of setovering towards described inlet, prevent that fluid from flowing into described piston chamber; And

When make described piston when the described second place moves to described primary importance by described second sealed member of setovering away from described outlet, allow fluid to flow out from described piston chamber.

12, method according to claim 10 further comprises:

First dividing plate that utilization is located between described inlet and described piston chamber prevents that described first sealed member from entering described piston chamber.

13, method according to claim 10 further comprises:

The second partition of utilization location between the described outlet outside prevents that described second sealed member breaks away from described piston chamber.

14, method according to claim 10 further comprises:

By backing out described piston piston is pulled down from the pump that described piston is moving, thereby release comprises the screw section of the outside of described piston chamber.

15, method according to claim 10 further comprises:

When by towards make described piston when the described second place moves to described primary importance away from the second outlet biasing the 3rd sealed member that is connected to described piston chamber, allow fluid to flow out from described piston chamber.

16, method according to claim 10 further comprises:

Thereby, prevent that fluid from flowing out from described piston chamber when forming sealing with it and make described piston when described primary importance moves to the described second place by allowing the 3rd sealed member to move towards second outlet that is connected to described piston chamber.

17, a kind of piston cartridge comprises:

The fluid containment device, it is used to hold fluid;

The fluid leading device, it is used for fluid is introduced described fluid containment device, and the contiguous described fluid containment device of wherein said fluid leading device is located and is provided fluid to enter the path of described fluid containment device by it;

The fluid ejector, it is used for fluid is drawn from described fluid containment device, and the contiguous described fluid containment device of wherein said fluid ejector is located and is provided fluid to leave the path of described fluid containment device by it;

Fluid displacement apparatus, it is used to make fluid to move, and wherein said fluid displacement apparatus to small part is positioned in the described fluid containment device and relatively near the primary importance of described fluid leading device and removable between the second place away from described fluid leading device relatively;

First baffle plate device, it is used to provide first dividing plate, and described first baffle plate device is positioned between described fluid displacement apparatus and the described fluid leading device;

First seal arrangement, it is used to provide the first fluid sealing, described first seal arrangement is positioned between described first baffle plate device and the described fluid leading device and is removable between described first baffle plate device and described fluid leading device, wherein when the contiguous described fluid leading device of described first seal arrangement location, it seals described fluid leading device substantially, and when contiguous described first baffle plate device of described first seal arrangement location, it allows fluid to flow into described fluid containment device;

The second partition device, it is used to provide second partition, the contiguous described fluid ejector of described second partition device location; And

Second seal arrangement is positioned between described fluid displacement apparatus and the described second partition device and is removable between described fluid displacement apparatus and described second partition device, wherein when the contiguous described fluid ejector of described second seal arrangement location, it seals described fluid ejector substantially, and when the contiguous described second partition device of described second seal arrangement location, it allows fluid to flow through described fluid ejector.

18, piston cartridge according to claim 17 further comprises:

Biasing arrangement, it is used for towards the described second place described fluid displacement apparatus of setovering, the contiguous described fluid displacement apparatus of wherein said biasing arrangement location.

19, piston cartridge according to claim 17 further comprises:

Guiding device, it is used to guide fluid to flow out to the needed position of described fluid containment device outside from described fluid output device.

20, piston cartridge according to claim 17 further comprises:

Restricting means, it is used to limit moving of described second partition device, the location, both sides at least in the contiguous described second partition device of wherein said device for limiting.

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