CN106103988A

CN106103988A - Axial plunger device

Info

Publication number: CN106103988A
Application number: CN201580013133.5A
Authority: CN
Inventors: 道格拉斯·A·赫明克
Original assignee: TOWICK CO
Current assignee: TOWICK CO; Torvec Inc
Priority date: 2014-02-07
Filing date: 2015-02-05
Publication date: 2016-11-09
Also published as: BR112016018015A2; EP3111087A1; US20200332782A1; JP2017508097A; US20160348672A1; WO2015120154A1; KR20160119815A

Abstract

A kind of axial plunger device, this axial plunger device can be as rotary valve that is pump operated and that include self centering.This device includes the static housing surrounding axle and rotary valve.Rotary valve and axle are attached to each other.When rotated, rotary valve is due to the elimination of the moment in pump and power and self centering.The pump of the present invention is plunger assembly.Valve is positioned at valve opening, and this valve opening is a part for clack box.Axle is positioned at clack box and this axle is attached to the flat surfaces of rotary valve at its far-end.Axle has the first rotation and rotary valve has the second rotation.During the operation of pump, first axle is often from the second journal offset.Pump is operated by means of reciprocating plunger by swash plate, and housing keeps static simultaneously.

Description

Axial plunger device

Cross-Reference to Related Applications

The application relates to and requires the U.S. Provisional Application No.61/937,166 submitting on February 7th, 2014 and in 2014 The U.S. Provisional Application No.62/093 that on December 17, in submits to, the rights and interests of 146, the full content of the two U.S. Provisional Application It is incorporated herein by reference.

Technical field

It relates to fluid dynamic and relate more specifically to the displacement via axial plunger device for the fluid.

Background technology

Axial plunger technology generally with non-rotating cylinder apparatus and rotary cylinder-block device (for example, rotating cylinder build hydraulic pump/ Motor, commonly referred to " rotary components ") implement.Conventional non-rotating cylinder pump figure 1 illustrates and rotary cylinder-block pump is at Fig. 2 Shown in.

The problem that non-rotating cylinder body stands the power on the axle of pump and swash plate.These power must be by loading ability of bearing.Unfortunately, make The power being used on the axle of pump and swash plate is unbalanced.If do not suppressed, out-of-balance force can cause quick pump to wear and tear.By In there is the demand to the big bearing for processing the unbalanced load in non-rotating cylinder body, therefore pump must be very big to accommodate Big bearing.

Owing to cylinder body absorbs the unbalanced power of the major part in non-rotating cylinder body, therefore these problems are in rotary cylinder-block Do not exist.Therefore, rotary cylinder-block device can be designed to little more than non-rotating cylinder body.Rotary cylinder-block designs the inherent shortcoming having It is: rotary cylinder-block has bigger rotating mass inertia.This shows as the power loss increasing, and is especially changing rotary speed Period.Within this technology, the device of construction needs the optional feature of accommodating rotary cylinder-block.This needs following apparatus: although this dress Put less than existing device, but this device is still bigger than desired device and heavier.Encapsulation and efficiency are by both performances Disadvantageous.

Content of the invention

This pump introduces fluid and in some embodiments by non-rotating cylinder body, is enabled flow through by rotary valve. Rotary valve connects with the multiple plunger hole continual fluid in entrance cavity and outlet plenum and cylinder body.

This pump is characterised by while allowing swash plate to rotate having on swash plate and the equilibrant force in pump generally. The distribution that fluid runs through pump makes the out-of-balance force in non-rotating cylinder pump balance, without especially big bearing.The enforcement of this pump Mode includes two-sided swash plate, and this allows the balance of all swash plate power.During operation, the size of this pump is no longer by rolling element axle The restriction of the existence held.This pump can the wider operating condition of process range and being used in high pressure and/or high displacement pump at pump When demonstrate size reduction in terms of greater advantage.The design of the pump of prior art and limited efficacy are in the need of very big bearing Want.This is no longer problem in the design.

The illustrative embodiments of the hydraulic pump of the present invention is to have the embodiment of multiple passage in axle.Owing to rotating The function of valve and axle is performed by single parts, and therefore passage eliminates the needs to rotary valve.The embodiment bag of hydraulic pump Include swash plate and self centering axle, wherein, swash plate have be attached to (slipper shoe) bottom first group of multiple piston shoes first Sidepiece, self centering axle can rotate at least one static cylinder body around the axis of himself.Self centering axle has many Individual passage, the plurality of passage is received, is guided and exhaust fluid.Self centering axle can during the operation of pump medially and partially Heart rotates.Fluid pressure on the passage of axle makes the power on axle and/or moment be balanced.

Swash plate is connected to axle and is configured to tilt with regard to the axis vertical with the axis of axle.The inclination of swash plate can be passed through Hydraulic means, machinery dog bone type assembly, electric device, gear train etc. realize.

Another embodiment relates to the pump with self-balancing axle.It is first smooth that swash plate has reciprocal general planar Surface and the second flat surfaces.Multiple first slippery boots assemblies and multiple second slippery boots assembly are attached to the first flat surfaces and second Flat surfaces.Fluid pressure on passage on axle makes the dynamic balance on all directions.Housing is by axle, swash plate and slippery boots assembly bag Enclose.Housing has at least one and is used for fluid from going out that pump is discharged with at least one for the entrance being received in pump by fluid Mouthful.

The axle of hydraulic pump is self centering.Exemplary hydraulic pump by include at least one static single type cylinder body and Axle, this axle can rotate in static cylinder body around the axis of himself.This embodiment of hydraulic pump also includes multiple first Plunger and multiple second plunger.Multiple first plungers and multiple second plunger are contained in cylinder body and are positioned at coaxial with axle In arch.Multiple plungers are positioned on the contrary end of swash plate.At least one (or first) cylinder body described surrounds multiple first post Plug and the second static cylinder body surround multiple second plunger.

The fluid stream running through pump being driven by the reciprocating motion to plunger for the swash plate and producing produce on axle power and/ Or moment.Multiple passages construction makes the power on axle and/or moment be balanced on axle.

Pump may be configured so that the axle of hydraulic pump has the valve being attached in axle and the passage along axle plays ratio and guarantees The least action that axle is centered more acts on.Passage is also configured to receive in the multiple favourable position along axle, draw Lead and exhaust fluid stream.In other words, in addition to making the passage of necessary minimal amount that axle centers, based on the fluid of pump Axle also can be added passage by the needs of stream.The embodiment constructing in like fashion will include at least one static cylinder body and encloses It is enclosed in the valve in this static cylinder body.Valve will include the axle extending through static cylinder body.Axle will have the length along axle Multiple passages.

The embodiment of hydraulic pump has two-sided swash plate.Swash plate has the first side being attached to bottom first group of multiple piston shoes Portion and be attached to the second sidepiece bottom second group of multiple piston shoes.First sidepiece of swash plate is substantially flat with the second sidepiece of swash plate OK.The parts of the first sidepiece being attached to swash plate are substantially right with regard to swash plate relative to the parts of the second sidepiece being attached to swash plate Claim.

Housing encapsulates swash plate.Swash plate is attached to multiple slippery boots assembly via fluid bearing part.Slippery boots assembly is positioned at swash plate On two sidepieces.Swash plate is anchored at relative to the fixed range of the end of axle by axle.Swash plate can be in place via pin anchoring.No Opinion is used for anchoring which kind of device of swash plate, and swash plate is all constructed to be permeable to hang down with respect to crooked or with axle the axis of axis of axle Straight axis is adjusted.Alternatively, in the case of fixing volumetric displacement, can be solid at a particular angle by swash plate Fixed.That is, swash plate not necessarily allows for regulation.

Another embodiment of pump has two-sided swash plate, and in this embodiment, multiple pumps are contained in single housing.This Embodiment has swash plate, and this swash plate has the first swash surfaces.First pump has multiple first component, the plurality of first Part includes being attached to the first swash surfaces bottom multiple first piston shoes.It is attached to multiple plunger bottom piston shoes.Each plunger holds It is contained in corresponding cylinder bore.Second pump includes multiple second component, and the parts of the plurality of second component and the first pump are basic Identical.Second pump part and the first pump part almost symmetry.The mid-plane of swash plate is the boundary line between each pump.

Single housing is one around the first pump and the second pump and cylinder bore with this housing.This pump includes for balancing The device of the one of the internal forces in the first pump and the second pump and/or moment.It is contemplated that single housing includes at least one Individual additional pump and this pump are configured to and the first pump and/or the second pump basic simlarity.The axle of additional pump will be arranged to and shell The first internal pump and the second pump are parallel.

In another embodiment, it is attached to axle to rotary valve heterogeneity so that only thrust and moment of torsion are at rotary valve and axle Between transmission.Axle is also coupled to swash plate.I.e., the sliding interface of swash plate and piston shoes is relative to the rotation with axle at swash plate angle The angle initialization of vertical plane is to angle of inclination, i.e. be fixedly coupled to axle or by swash plate controlling organization with variable Mode control.Wobbler promotes the reciprocating motion of plunger by slippery boots assembly.In one and half portions of swash plate, plunger by from Its respective cylinder bore is extracted or is pulled out, and in another half portion, plunger is extended to or shifts onto in its respective cylinder bore.

Rotary valve is to have two single fluid passages i.e., and respectively suction inlet and discharge outlet is big Cause cylindrical body.Two passages all connect with one or more plunger holes on curved surface.The curved surface of two passages Toward each other and each occupy the half less than rotary valve circumference.Rotary valve is attached to axle so that pump inlet is to from post The plunger hole of those plungers that consent is extracted opens wide and pump passing away is to the plunger of those plungers extending in plunger hole Hole is opened wide.Therefore, when plunger pulls out from hole, rotary valve allows the fluid from the suction chamber of valve to be transferred to corresponding plunger In the volume of the increase in hole.But, in the plunger hole in another opposite side of pump shaft line, fluid is forced through passing away Leave plunger hole and reach in the discharge chamber of valve.

Change to the design of rotary valve is possible.The embodiment of disclosed pump includes having the clack box of one Housing, this clack box surrounds rotary valve.Rotary valve includes axle, passage section and seals section.Seal section and have semicircular close Spine-sealing portion.Rotary valve includes first axial face seal and of the first flat end and the second flat end being positioned at rotary valve Two axial face seal and be positioned at rotary valve the sidepiece relative with semicircular sealing spine on high pressure discharge section and The entrance section being positioned on the first sidepiece of rotary valve.Rotary valve is that generally cylindrical and semicircular sealing spine is to rotation Valve surrounds less than 360 deg.Rotary valve has clack box bonding part (that is, sealing spine) and recessed portion.

Operating clearance is positioned at high pressure and discharges between section and clack box.The width of operating clearance depends on discharging section at high pressure The power of the direction applying along semicircular sealing spine for the place.Semicircular sealing spine is maintained at away from clack box basic during operation At constant operating distance.The width of operating clearance additionally depends on the girth of axle rotating speed and rotary valve.

Another embodiment of pump includes valve opening, and rotary valve is surrounded by this valve opening.Rotary valve has at least one axial face Seal and at least one sagittal plane seal.Operation sealed airspace is positioned between sagittal plane seal and valve opening.Operation seals Space keeps the thickness being basically unchanged during the operation of rotary valve.Delivery space is positioned between rotary valve and hole.Rotary valve leads to Cross along semicircular sealing spine direction apply power and bias and this power determine operation sealed airspace width.Rotary valve Including axle.Sagittal plane seal have semicircular seal member and with axle almost coaxial, this axle includes access road and row Go out passage.It is interesting to note that sagittal plane seal is allowed to the free degree moving relative to axle so that sagittal plane seal is not total It is coaxial with axle.

The another embodiment of pump includes the housing with valve opening and clack box.Axle is positioned at clack box and rotary valve is positioned at valve In hole.Axle is attached to the flat surfaces of rotary valve at far-end.Axle has the first axle being offset from one another and the second axis.Behaviour During work, the dead in line of the second axis and valve opening and first axle are from the disalignment of clack box.

Rotary valve includes high-pressure outlet and low-pressure inlet.Axle can be along the direction skew contrary with the high-pressure outlet of rotary valve And also can be along the direction skew of the high-pressure outlet towards rotary valve.

Clack box contact surface contact clack box on axle for the axle.Bearing is positioned in clack box and contacts table with axle at clack box Contact at face.

Being disposed with multiple cylinder body in clack box, the plurality of cylinder body is arranged abreast and the mode in the circle around valve opening is arranged And it is arranged to coaxial with valve opening.Rotary valve is not coaxial with valve opening with valve opening almost coaxial and axle.Axle and rotary valve are overall Formula.

Rotary valve makes high pressure load balance.Valve can be configured to eliminate out-of-balance force, and this makes valve move away its rotary shaft Line.Any out-of-balance force on valve can damage lubricating fluid envelope barrier, and this will cause metal between rotary valve and valve opening and gold Belong to contact.This can make valve cling valve opening, thus destroys rotating member.

Rotary valve is by high-pressure fluid conveying or guides to the thrust chamber between valve and clack box thrust shelf, to balance on axle Axial load.In one embodiment, the area at valve/interface, fluid thrust chamber is equal to the sum of all plunger/fluid boundarys Only about half of.Most of axial load on axle is contained in cylinder body.Roller elements thrust bearing be enough to control total axial load The sub-fraction between axle and external shell of lotus.

In the present embodiment, low-pressure fluid by entrance enter pump and enter in valve entrance cavity in.This fluid Continue through via valve inlet passageways and reach multiple plunger hole.Each plunger being connected with valve inlet passageways is forced off post Consent.As axle-valve continues to rotate, plunger is forced in plunger hole, thus compresses fluid.Now, plunger hole start to Valve passing away opens wide.Valve passing away allows the high-pressure fluid from plunger hole to continue through and reaches discharge chamber, this row Going out in chamber, high-pressure fluid leaves pump by outlet subsequently.Power needed for mobile plunger is carried by the input torque inputting to axle-valve Supply.This moment of torsion is transferred to swash plate.Swash plate is forced into swash plate due to swash plate relative to the inclination (referred to as swash plate angle) of axle-valve High pressure half portion on piston shoes in.Slippery boots assembly is forced in plunger subsequently, plunger and the fluid communication in plunger hole.Should Process produces a different set of power/moment.Axial load is carried by swash plate, is transferred to valve-axle by the axial load that swash plate carries. Equal and contrary axial load is carried by thrust chamber by valve-axle, thus realizes zero net axial load.Moment is held by swash plate Carry, the moment that swash plate carries is transferred to valve-axle.Equal and contrary moment is entered by valve passing away and valve by valve-axle Pressure reduction carrying between mouth passage.Last power/moment is the moment with regard to rotation, and this moment is by driving needed for valve-axle Input torque work.Therefore, axle-valve and every other rotating member are balanced.The balance of rotating member is independent of swash plate Angle control and/or piston shoes hold-down mechanism.

In the pump of prior art, the displacement of high-pressure fluid causes the bigger thrust load on swash plate and clack box or axial Load, thrust load or axial load are transferred to pump external shell subsequently.In addition, in the pump of prior art, thrust load is produced Bigger separating force between raw external shell parts, thus increase required clamping load.This thrust load is divided equally multiple It is disadvantageous between parts, is because which increasing the overall dimension of pump and weight, on the contrary, the present invention utilizes single type cylinder Body, in all axial loads are contained in cylinder body by this single type cylinder body and substantially reduces the needs of clamping load, and this enters And allow to reduce pump size and weight.

Non-rotating cylinder body is incorporated to by pump.Reciprocate through and swash plate is fixed to rotary shaft realization, and this coiling is single Axis rotates with the angle relative to this single axis, to realize reciprocating motion in pump for the plunger.Generally cylindrical rotary valve There is at flat surfaces suction or the introducing region that the portion of being externally supplied with low-pressure fluid connects.This introducing portion passes through valve and rotation The inlet passage being configured to alternately connect with one or more cylinder bore on the curved surface of rotary valve.At rotary valve Contrary curved surface on be recessed output area or the discharging area of rotary valve.Output area with one or more Cylinder bore alternately connects, and output area is from the conduit of the output of pump for high-pressure fluid.

This pump introduces fluid into the center line by rotary valve, and fluid advances along more direct and consistent path, This reduce possibility and the pressure loss therefore reducing between access road and plunger hole that fluid velocity increases.So And, this valve opens wide all the time to the cylinder body conduit leading to plunger hole.

Rotary valve balances high pressure load.This eliminates the power that valve otherwise may be made to dish out away from center.Rotary valve is permissible Protection lubricating fluid envelope barrier, thus stop the metal between rotary valve with cylinder body to contact with metal.

The spherical head of each plunger can be directly mounted to bottom conventional piston shoes, and by pressure strip and swash plate Flat surface portion keeps effective sliding contact.

The non-rotating cylinder body axial pump previously repeated needs bigger bearing.The pump large and bulky of gained.Institute is public herein The embodiment opened reduces size and the weight of similar 1/3rd, and is not losing energy by other pumps various remodeling May reduce more in the case of power or efficiency.This pump allows larger-diameter plunger to have shorter stroke.Plunger can be In the case of not sacrificing ability shorter and this allow that shorter pump.In not being entered by the load that working fluid causes to plunger In the case of row balance, load must be by mechanical bearing (that is, thrust bearing) balance.In the pump of prior art, this The mechanical bearing with short and wide plunger must be very big.But, owing to this pump uses fluid bearing part, therefore short and wide Plunger be available, without increase pump size.

Swash plate is configured to regulate the haul distance of multiple plunger.The device at the angle of inclination for regulating swash plate can be machine Tool or hydraulic pressure or a combination of both.If hydraulic pressure, the device in order to regulate the angle of inclination of swash plate can wrap Including multiple capacity part hydraulically filled, the plurality of capacity part hydraulically filled is constructed to respond to the hydraulic pressure in capacity part The change of fluid and the angle of inclination that regulates swash plate.The rotary valve of pump preferably includes moment balancing controls.Moment zeroing dress Putting the high-pressure channel with balance, the high-pressure channel of this balance is arranged to during rotation receive high-pressure fluid.

Each plunger in multiple plungers has working fluid end.The flat end being exposed to high-pressure fluid of rotary valve Effective (only) surface area be equal to the high pressure being exposed to high-pressure fluid of each plunger in (or being nearly equal to) multiple plunger The sum of the area of plane of end.Swash plate is connected to corresponding plunger by multiple slippery boots assemblies.It is sliding that fluid bearing part is positioned at each Between boots assembly and swash plate.Fluid bearing part is fluidly coupled to the high voltage end of corresponding plunger.

Axle and rotary valve are designed to move freely through with regard at least four free degree.This hydraulic pump have static cylinder body and It is positioned at the valve of static cylinder body.Valve be connected to the axle in static cylinder body and with this axle almost coaxial.Valve can be around axle Axis rotates and this valve is constructed to be permeable to offset with regard to four frees degree relative to the axis of axle.

Connecting structure between valve with axle becomes restraint to transmit into moment of torsion and the edge of the rotation with regard to axle from axle to valve The thrust load of rotation.Valve is put down by check leak rate according to the power on valve and/or moment in rigid body Weighing apparatus.

Another embodiment of hydraulic pump is designed to the embodiment with driving key.This embodiment has axle-valve Assembly.Interaction between driving key and keyway for the valve is connected to axle.Connection between valve and axle is via polytype Any securing member in securing member keeps.Interact at least one free degree being constructed to valve offer relative to axle.Degree (or The free degree, the free degree if more than) it is being configured on the linear direction vertical with the rotation of axle.Swash plate is even It is connected to axle.Swash plate is as axle rotates and is configured to via the device for making swash plate tilt with regard to the axle vertical with the axis of axle Line tilts.

Rotary valve is elongated cylinder, rotary valve highly preferable big than the diameter of rotary valve.High pressure interconnection is simultaneously Put in the side surface of rotary valve.Low pressure transitional region is positioned in the side surface of rotary valve and contacts with high-pressure channel and from height Pressure passageway extends preset distance.

Flat end with rotary valve is one.The surface area that hydrodynamic thrust bearing discharges thrust chamber is equal to many The gross area of the end surfaces of individual plunger only about half of.

Multiple slippery boots assemblies are fluidly coupled to swash plate.Slippery boots assembly each includes piston shoes bulb, piston shoes neck and piston shoes Bottom.Pressure strip keeps the fluid between slippery boots assembly and swash plate to couple.Pressure strip includes multiple recess, in the plurality of recess Each recess configuration become to engage corresponding slippery boots assembly.Pressure strip is prevented from pivoting.

Another embodiment is the embodiment of the rotary valve/axle separating.The rotary valve of the embodiment separating is to rotate Tubbiness valve.One of advantage of present embodiment advantage is by using the imitation valve of bucket and the disc valve phase more like dish Eliminate cantilever force on the contrary.This is owing to dish is easily affected by cantilever force.Present embodiment includes the axle with swash plate.Axle Rotate in housing with swash plate.Multiple plungers vibrate in response to the rotation of axle and swash plate.Rotary valve is coaxial with axle and is revolving It is securely attached to axle at the flat end of rotary valve.Rotary valve configuration becomes around the axis rotation sharing with axle.

The entrance that is advantageously characterized by of present embodiment centers along the main shaft of pump.One advantage of this configuration is The turning number of the access road in rotary valve can reduce.Therefore, the possibility producing air pocket reduces.Present embodiment includes Axle and the rotary valve being positioned at pump case.Rotary valve is coaxial with axle and is connected to this axle.Passage is connected to entrance and has Bending or the travel path turned not less than 90 degree.At least one high-pressure channel is positioned in rotary valve.

Pump case has the clack box of one and multiple cylinder body.Cylinder bore is fluidly connected to rotary valve high-pressure channel.In rotation When rotary valve rotates.Hole and pump intake and passage and pump discharge alternately fluidly connect.

Present embodiment includes the clack box housing with multiple plunger hole.Rotary valve is rotatably contained in clack box Housing is interior and includes that entrance aperture and access road, entrance aperture and access road succeedingly and are fluidly connected to cylinder body Hole.Access road has the axis through rotary valve.Access road has the maximum bend angle of about 90 degree to avoid excess Fluid separate, therefore increase the fluid velocity by passage.

Flow and flow that swash plate controls at least in part through entrance are also controlled by the rotary speed of axle.Rotary valve bag Include multiple high pressure interconnections in the side surface of rotary valve for the juxtaposition.High-pressure channel is fluidly connected to high pressure interconnection simultaneously And extend preset distance from high pressure interconnection.The flat end of rotary valve is arranged, this row for the existence discharging thrust chamber Go out the axial force that thrust chamber is configured on ballast pump.

Connection between rotary valve and driving element (axle) can be via rotary valve keyway and one or more c clevis. The advantage of this structure is that the thrust load of plane is carried by the interface between keyway, c clevis and axle and this interface provides and uses In the device that moment of torsion is transferred to from driving element rotary valve.Connection between the keyway of rotary valve and the key of axle is by transmitting torque from shaft It is transferred to rotary valve.

Connecting through at least one c clevis and preferably being locked by a pair c clevis between axle and rotary valve, described At least one c clevis or at least one pair of c clevis described are coaxial with axle.At least one c clevis described or at least one pair of c clevis described Engage the recess in axle and the corresponding recess in rotary valve.Keyway can have at least one in the flat surfaces of rotary valve The free degree.

Rotary valve includes combining the parts that being configured in the surface of rotary valve makes to act on the dynamic balance on rotary valve. These parts can be also configured to contribute to balancing the moment with regard to whole pump.Under bottom line, parts are configured to ballast pump Interior revolving force and axial force.

Axle-valve the pump (axle-valve pump with one) separating can include precompressed recess and decompression in the surface of rotary valve Recess.Such advantage is the reduction of pump noise.Except other aspects, pump noise is to be caused by the Rapid Variable Design of fluid pressure 's.

This embodiment of pump includes having the clack box of main aperture and is positioned at the rotary valve of clack box housing.Rotary valve includes height Extrude mouth and low pressure outer surface.Rotary valve has the rotation of the center line along main aperture.At least one precompressed recess fluid Be connected to the entrance sidepiece of high-pressure outlet.

Rotary valve also includes entrance in one of its flat surfaces flat surfaces.Entrance is with regard to the rotary shaft of rotary valve Line centers.Rotary valve also includes interconnection in its side surface bending.Act on rotary valve due to high pressure fluid stream On power be balanced by interconnection.At least one high-pressure area and at least one area of low pressure are arranged by interconnection. High-pressure area and area of low pressure become to eliminate to act on around rotary valve configuration the moment forces on rotary valve, the institute's moment on valve and The balanced region of power test on determine or pass through equation defined location.

The advantage of single type cylinder body as described above is to act in the multipart housing of the cylinder body of prior art Seam on power be eliminated.Cylinder body accommodates multiple cylinder bore.Plunger is slidably positioned in each cylinder bore.Cylinder body is whole Body formula and cylinder bore and cylinder body be one.

Hydraulic pressure slippery boots assembly fluid feed channel runs through the whole length of slippery boots assembly and exists.In addition, in multiple plungers Each plunger be respectively provided with plunger fluid feed channel, this plunger fluid feed channel be fluidly coupled to slippery boots assembly fluid supply To passage and be fluidly coupled to plunger hole in addition.

Disclosed theme utilizes the stream allowing the relative motion between the valve/axle/swash plate of pump and cylinder body/clack box/housing Body supporting member.This configuration reduces the load on all supporting members in device, and this in turn reduces during operation is additional Supporting member loses.

The reduction of supporting member load is the effect of the balance between fluid force and the structural response of those load.Due to from The pressure of fluid and/or energy are converted into mechanical force or become load, therefore when mechanical energy is transferred to fluid from drive motor Fluid force occurs in pump.By this design, between plunger axial force and the second power, there is balance, wherein, plunger axial force Being produced by the reaction of the fluid pressure of the motion of opposing plunger, the second power is (described flat by the flat surfaces acting on valve/axle Flat mask has common axial members) on high-pressure fluid produce reaction force.Resulting net force (that is, aforesaid first power and The difference of the size of two power) it is continually changing during the operation of device.The time dependent imbalance of these power needs device The structural member in order to support net residual force and moment.

The advantage of non-rotating cylinder body technology includes less quality and less assembly dia, thus provides less rotation Quality and therefore less rotary inertia, this improves gross efficiency when operating under the conditions of unsteady state.In addition, cylinder body can For use as device case, it is thus eliminated that add separate part i.e., as the need of housing of the structural elements of device Want.

This pump utilizes inevitably leakage (that is, the fluid shifting under high pressure, this fluid of working fluid and working fluid Otherwise leakage between all parts in pump is only expelled to groove/cistern, therefore presents the supplementary loss of 100%) Balance aforesaid rotating member (that is, axle, swash plate and valve；And for coupling and/or controlling the mechanism of axle, swash plate and valve) Internal forces and/or moment.This pump installation makes the utilization predetermining the leakage that (by design) controls of working fluid minimum Change the internal forces balance producing when under high pressure being shifted in the following manner making on mechanical part by working fluid: in this way Do not need described working fluid in order to produce the extra attached of load resistance supporting member (that is, in order to support hydrostatic bearing) Add discharge.This has the effect of the gross efficiency improving device.Therefore, this pump does not needs moving element supporting member (that is, roller elements The bearing of type) use.For the load applying and rotary speed, typical axially directed plunger assembly is in diameter, weight and becomes Present aspect needs bigger bearing.

Each embodiment of disclosed pump has the valve geometry of tubular, and this geometry has the enclosed watch of bending Face/supporting surface.Valve plate (that is, is used as what the working fluid of fluid film separated as smooth supporting member by conventional technique Two flat sealing surface) use.The advantage of cylindrical form is: when load in off-axis condition (that is, cylinder body relative to The eccentric position in hole) under operation when, space between cylinder body and its hole produces variable gap size.This so during rotation Produce the wedge shape effect of working fluid.This phenomenon is referred to as wedge effect (seeing Fig. 3) and produces execution two effect Uneven pressure distribution in load region.First and first and foremost, wedge effect provides and phase equal with the load being applied Anti-reaction force.Second, wedge effect is when cylinder body (or axle) rotates by new fluid draw to the region loading, and this supplements Fluid loss due to the pressure reduction between the region that loads and remaining fluid cavity.

Disclosed pump is by valve and bearing of journals Mechanism Combination to parts.From be discharged to suck (across supportedly Band) axial leakage stream provide the mode of heat transfer, and thus eliminate the fluid (lubricant) of pressurization by special The needs to axle journal zonal area for the mouth row.

Brief description

Fig. 1 shows the conventional pumps with non-rotating cylinder body；

Fig. 2 shows the conventional pumps with rotary cylinder-block；

Fig. 3 shows the rotary valve standing wedge effect；

Fig. 4 shows the first embodiment of self-balancing hydraulic pump；

Fig. 5 shows the multiple plungers being arranged in archedly in the hydraulic pump of the present invention；

Fig. 6 shows the first embodiment of the hydraulic pump of the swash plate with inclination；

Fig. 7 shows the second embodiment of hydraulic pump；

Fig. 8 shows the 3rd embodiment of hydraulic pump；

Fig. 9 is the sectional view of the hydraulic pump shown in Fig. 5；

Figure 10 is another sectional view of the hydraulic pump shown in Fig. 5；

Figure 11 A to Figure 11 B is the detail view of the rotary valve of the hydraulic pump of Fig. 5；

Figure 12 is the detail view of swash plate；

Figure 13 is the detail view of slippery boots assembly；

Figure 14 is the view of two-piece type rotary valve；

Figure 15 is the rotary valve showing noticeable wear；

Figure 16 is the sectional view of pump, shows the rotary valve of the first form；

Figure 17 A is the first view of the sealing section of the rotary valve shown in Figure 16；

Figure 17 B is the second view of the sealing section shown in Figure 17 A；

Figure 17 C is the sectional view of the sealing section of Figure 17 A, shows the pressure drop on surface across this sealing section；

Figure 17 D is the first view that the sealing section of Figure 17 A is attached to rotary valve；

Figure 17 E is the second view that the sealing section of Figure 17 A is attached to rotary valve；

Figure 18 is for using the first sectional view of the whole pump of the rotary valve of Figure 16；

Figure 19 is for using the second sectional view of the whole pump of the rotary valve of Figure 16, wherein, position from Figure 18 for the rotary valve Put rotated ninety degrees；

Figure 20 is the top view that the rotary valve of Figure 16 and sealing section are positioned at valve opening；

Figure 21 is the sectional view of pump, shows the rotary valve of the second form；

Figure 22 A is the first view of the sealing section of the rotary valve being attached to Figure 21；

Figure 22 B is the second view of the sealing section of the rotary valve being attached to Figure 21；

Figure 23 is the sectional view of the sealing section of Figure 21, shows the pressure drop on surface across this sealing section；

Figure 24 is the top view that the rotary valve of Figure 21 and sealing section are positioned at valve opening；

Figure 25 is the sectional view of pump, shows the rotary valve of the third form；

Figure 26 is the sectional view of the rotary valve of the pump shown in Figure 25 and axle；

Figure 27 is axial face seal embodiment and sagittal plane seal embodiment；

Figure 28 is the partial view of rotary face seal；

Figure 29 is the stereogram of axial face seal；

Figure 30 shows the two-sided of the sagittal plane seal embodiment with Figure 27 and rotary face seal embodiment Pump；

Figure 31 is valve and the sectional view of sagittal plane seal, and this sectional view show at the sagittal plane seal of valve Barometric gradient；And

Figure 32 is the sectional view showing the O-ring relevant with the passage in valve.

Detailed description of the invention

Fig. 4 shows hydraulic pump 2.Pump 2 includes housing 4.It is extended with axle-valve 6 along the whole length of housing 4.Axle-valve 6 Power in permission pump 2 and/or the balance of moment.Owing to power and/or moment are balanced, therefore reduce the mechanical bearing in pump Necessity.Accordingly, because roller elements bearing is unnecessary in pump 2, the therefore construction of pump 2 and ability during operation It is not limited to the ability of any rolling element bearing.

This embodiment of pump 2 has multiple passage 10a and 10b in axle-valve 6.Run through fluid stream and the swash plate 8 of pump 2 Rotate the power producing on axle-valve 6 and/or moment.Fluid stream is the result of wobbler.Plunger passes through they and wobbler Engage produce reciprocating motion and cause fluid stream.Therefore, wobbler (with fluid stream) produces the power on pump.Multiple passages 10a and 10b constructs in axle-valve 6 so that power and/or moment on axle-valve 6 are balanced.

It is beneficial and discussed in detail below on other occasions with the rotary valve that axle separates.But, at this In embodiment, passage 10a and 10b and axle-valve 6 are one and owing to the function of rotary valve and axle is by single parts Axle-valve 6 performs and eliminates any needs to single rotary valve.Not there is the normal of rotary valve as disclosed herein Advise non-rotating cylinder pump figure 1 illustrates.

Swash plate 8 is connected to axle-valve 6 and is preferably configured to hang down with regard to the axis of axis 28 axis 28 and axle-valve 6 Straight inclination.Swash plate 8 has the first sidepiece 12, and the first sidepiece 12 couples multiple first slippery boots assembly 14.Slippery boots assembly 14 Figure 5 illustrates with contacting between swash plate 8.Axle-valve 6 in housing 4 with regard to physical axis 16 self centering of himself, That is, the axis of symmetry of the rotation of axle-valve 6 and axle-valve is as far as possible in line.Swash plate 8 is two-sided swash plate.Swash plate 8 is dish Shape and the plane symmetry with regard to the pars intermedia through this dish.First sidepiece 12 preferably flat surfaces.Swash plate 8 has Two sidepieces 20, the second sidepiece 20 is also preferably flat surfaces.First sidepiece 12 of swash plate 8 and the second sidepiece 20 are opposite each other. Multiple second slippery boots assemblies 50 are attached to the second sidepiece 20 of swash plate 8.

Use in two-sided pump for the wedge shape swash plate is better than prior art, but, in this pump 2, the first sidepiece 12 of swash plate With the second sidepiece 20 of swash plate each other close to parallel.First sidepiece 12 is parallel utterly each other with the second sidepiece 20 is Unnecessary.But, the first sidepiece 12 and the second sidepiece 20 are closer to parallel, and power on axle-valve 6 and/or moment will be closer to Complete equipilibrium.

Each slippery boots assembly in slippery boots assembly 14 all includes plunger 18.Housing 4 is used as the cylinder body of each plunger 18.At pump In 2, while axle-valve 6 and swash plate 8 rotate, housing 4 is irrotational and each plunger 18 keeps circumference static.This with The prior art pump that wherein cylinder body rotates is contrary.

With reference to Fig. 6, multiple first slippery boots assemblies (slipper assembly) 14 are attached to the first sidepiece 12 of swash plate 8 simultaneously And multiple second slippery boots assembly 50 is attached to the second sidepiece 20.The end of each slippery boots assembly 14 is bottom piston shoes 24.Piston shoes Bottom 24 can be along the surface sliding distance 44 of swash plate 8.Bottom piston shoes between 24 and the sidepiece 12 of swash plate 8 and sidepiece 20 via Fluid bearing part couples.Therefore, 24 freely slide along the surface of swash plate 8 bottom piston shoes.

Pin 22 is anchored at swash plate 8 at the fixed range relative to the end of axle-valve 6.No matter being used for anchoring what of swash plate 8 Planting device, swash plate 8 is all constructed to be permeable to crooked relative to the axis of axle-valve 6 around axis 28 axis 28 or is perpendicular to axle-valve The axis regulation of 6.The angle of inclination increasing or reducing swash plate 8 makes the volumetric displacement of hydraulic pump 2 i.e., axle each rotation Fluid volume discharge capacity adjusted.The angle of inclination of swash plate 8 is bigger, and the volumetric displacement of pump 2 each rotation is bigger.Tiltedly When the angle of inclination of dish 8 increases, the stroke of each plunger in plunger 18 in slippery boots assembly 14 and 50 all increases.Therefore, hold The plunger hole 48 putting each plunger 18 can accommodate more fluid, with thus increase volumetric displacement.

For actuating plunger 18, axle-valve 6 rotates around its axis 16.The rotation of axle-valve 6 makes swash plate 8 rotate around axis 16. When swash plate 8 tilts, swash plate 8 makes plunger 18 along the respective axle of each plunger 18 with the interaction of slippery boots assembly 14 and 50 Line moves back and forth.Interaction between each slippery boots assembly 14 and 50 and swash plate 8 by swash plate 8 and slippery boots assembly 14 and The existence of the fluid bearing part between 50 and strengthen.Fluid bearing part is by the high-pressure spray of the central portion feeding through plunger and piston shoes Body provides.

Swash plate 8 can tilt around the axis 28 of pin 22.Be operatively connectable to swash plate 8 be for make swash plate 8 relative to The rotation 16 of axle-valve 6 tilts the device 32 of (that is, the position of angulation).Device 32 for making swash plate 8 tilt can be all As hydraulic jack or hydraulic cylinder etc hydraulic means, in response to machinery input mechanical dog bone type assembly, electric device, tooth Any one in wheel system or its any combination.Axle-valve 6 is easy to occur unintentionally at the run duration of pump 2 but sometimes can not keep away The eccentric rotary (and Concentric rotation) exempted from.It is therefore advantageous that make axle-valve 6 self centering.As shown in Figure 5, multiple passages 10a and 10b runs through pump 2 and receives fluid around axle-valve 6, guide fluid and from axle-valve 6 exhaust fluid.Multiple plungers 18 respectively with The coaxial mode of axle-valve 6 positions archedly.Multiple plungers 18 are divided into two groups and the two groups relative ends laying respectively at housing 4 Engage in portion and respectively with sidepiece 12 and the sidepiece 20 of swash plate 8.

Housing 4 has at least one and is used for fluid with at least one for the access road 36 being received in fluid in pump The exit passageway 38 discharged from pump 2.It is positioned at the passage 10a and passage 10b of each end of axle and be separated by substantially one hundred eight ten degree.

As observed in figure 6, fluid enters housing 4 at access road 36s and proceeds to low pressure chamber 46. Fluid enters multiple plunger hole 48 via low pressure port 40a and 40b and low-pressure channel 10b (seeing Fig. 4).Rotate at axle-valve 6 When, low-pressure channel 10b is continuously aimed at low pressure port 40a and 40b.High-pressure channel 10a is right constantly with high-pressure mouth 42a and 42b Accurate.High-pressure mouth 42a and 42b is connected with exit passageway 38 via pipeline 52a and 52b.

Act on the power on axle-valve 6 (mainly being caused) by the moment being produced by the high-pressure spray muscle power on plunger by leading to The geometry of road 10a and 10b and position balance.With further reference to Fig. 4, when passage 10a engages with high-pressure mouth 42a, passage 10b passage 10b is dynamically contrary with passage 10a, i.e. this makes the dynamic balance on pump engage with low pressure port 40b.This is Because making the effect of slippery boots assembly opposite each other (that is, when tiltedly owing to slippery boots assembly is in substantially contrary position on swash plate 8 When dish 8 tilts and rotates, a slippery boots assembly skids off its hole, thus produces vacuum, and contrary slippery boots assembly slides into its hole In and contribute on the fluid be positioned at hole produce high pressure).Effect is: the power being caused by the fluid stream in pump 2 on pump 2 makes The dynamic balance of the slippery boots assembly 14 and 50 on swash plate 8.

The sidepiece 12 and 20 of swash plate 8 due to swash plate 8 relative to the inclination (referred to as angle of inclination) of axle-valve 6 to swash plate 8 Slippery boots assembly 14 in high pressure half portion applies pressure.Each slippery boots assembly the 14th, 50 each piston shoes bottom 24 be forced subsequently to often Individual corresponding plunger 18 applies pressure, plunger 18 and the fluid communication in plunger hole 48.As shown in Figure 4, this process produces four Individual different power/moment (F_1,u, F_1,l, M₁, M₂).Axial load (F₁) carried by swash plate 8.Axial load has equal and contrary Two component (F_1,uAnd F_1,l).The alignment of back-to-back plunger exist compromise.The complete equipilibrium of axial load can pass through zero Transposition (that is, misalignment) realizes, and the plunger replacing causes the net axial load of non-zero.But, the transposition of back-to-back piston carries Having supplied enough balances of axial load, the advantage of transposition is that flowed fluctuation (that is, vibration, noise, pressure/flow pulsation etc.) can Significantly to reduce (that is, the half close to zero amplitude replacing).

Radial load (F₂) carried by axle-valve 6.Radial load has two component (F_2,uAnd F_2,l).These component F_2,uWith F_2,lEqual and opposite each other, thus realize zero net radial load.Moment (M₁) carried and transmitted by pivotal pin 22 by swash plate 8 To axle-valve 6.Equal and contrary moment (M₂) held by the pressure reduction between high-pressure channel 10a and low-pressure channel 10b by axle-valve 6 Carry (M₂By F_2,u&F_2,lProduce).Another power/moment is the moment (M around rotation_z), moment (M_z) react on drive shaft- Input torque needed for valve 6.Therefore, axle-valve 6 and every other rotating member are balanced.The balance of rotating member is independent of inclining Rake angle.

Housing 4 shown in Fig. 4 and Fig. 6 is the two-part housing including part 4a and 4b.But, housing is permissible It is all-in-one-piece or housing can be made up of many parts.It if housing 4 is made up of many parts, then is of value at each parts Between static seal such as o type circle or packing ring are set.Each parts can connect via flange or socket connection keeps together. By the configuration of two parts, the first static housing/cylinder body 4a surrounds multiple first plunger and the second static housing/cylinder Body 4b surrounds multiple second plunger.

As shown in fig. 4 and fig. 6, it is attached to the parts of the first sidepiece 12 of swash plate 8 relative to being attached to the second of swash plate 8 The parts of sidepiece 20 are with regard to swash plate 8 almost symmetry.But, pump disclosed herein is not limited to the two-sided structure shown in Fig. 4 and Fig. 6 Type.As shown in Figure 7, it is contemplated that the embodiment of one side pump 402.In one side pump 402, swash plate 408 is configured to be positioned at pump 402 An axial end portion at.In this case, owing to contrary groups of slippery boots assembly not occurring in the present embodiment, Therefore fluid bearing part 403 is more necessary.By comparison, the slippery boots assembly 414 of single group is employed.Therefore, it can make stream Muscle power and the moment and the power that are produced by the rotation of swash plate are zero.In order to compensate axial force, can be by recess 415 or similar cutting Mouth interpolation engages to axle-valve 406 and with the edge 417 of housing 404.

It can be envisaged that single housing include at least one additional pump (not shown) and described at least one Additional pump is configured to and the first pump and/or the second pump basic simlarity.Additional pump will be with the first pump and the parallel status of the second pump In housing.Therefore, multiple pumps are contained in single housing so that two or more axle-valves be positioned at housing and and that This is parallel.Parallel configuration is unnecessary.The operation of each pump in housing may be completely independent of other pumps in housing Operation.

Another embodiment of this hydraulic pump is to be designed to axle-valve 6 with regard at least three free degree and up to four The embodiment of free degree action.There are two linear DOF can with around at least one of the axis vertical with linear DOF Rotary freedom.

The Additional embodiments of the pump 502 of the present invention shown in Fig. 8 to Figure 12 and this embodiment be its axis and The embodiment that valve not combines as previous embodiment.Referring specifically to Fig. 8 and Fig. 9, the parts of pump 502 include pump case Body 504 (shown in Fig. 8), the 512nd, pump case 504 is equipped with axle the 506th, swash plate the 508th, pressure strip the 510th, one or more c clevis Rotary valve the 514th, cylinder body the 516th, clack box is the 518th, for setting swash plate control connecting rod the 520th, multiple plungers 522 of the angle of swash plate 508 With multiple slippery boots assemblies 524.Each slippery boots assembly in slippery boots assembly 524 includes bottom piston shoes the 526th, piston shoes bulb 528 and sliding Boots neck 530, each piston shoes neck 530 is connected to corresponding piston shoes bulb 528 by bottom piston shoes 526.

Axle 506 is along the central axis positioning of pump case 504.One end of axle 506 extends to the outside of pump case 504 And including spline 532.Spline 532 is toothed gear for being attached to motor, crank, flywheel or some other motions Transmission mechanism.Axle 506 is held in place by multiple bearings of each end being positioned at pump 502.

Connecting structure between valve 514 with axle 506 becomes and will be constrained to the rotary shaft with regard to axle from axle to the transmission of the power of valve The moment of torsion of line and the thrust load along this rotation.Valve 514 passes through in check according to the power on valve 514 and/or moment Leak rate is balanced in cylinder body 516.

Hydraulic pump 502 introduces fluid by non-rotating cylinder body and enables flow through rotary valve 514.Rotary valve 514 with enter Mouthfuls 536 and outlet 612 and cylinder body 516 in multiple plunger holes 546 continual communication.

In embodiments, with reference to Figure 10 and Figure 11 A to Figure 11 B, low-pressure fluid enters into entrance cavity by entrance 536 Pump is entered in 602.This fluid continues through via valve inlet passageways 614 and reaches multiple plunger hole 546.With valve inlet passageways 614 each plunger 522 being connected are forced off plunger hole 546.When plunger hole 546 is closed relative to valve inlet passageways 614, Low-pressure fluid is trapped.As valve 514 continues to rotate, plunger 522 is forced in plunger hole 546, thus in compressing hole 546 Fluid.Now, plunger hole 546 starts to open wide to valve passing away 616.Valve passing away 616 allows the height from plunger hole 546 Pressure fluid continues through and reaches discharge chamber 618, and in discharging chamber 618, high-pressure fluid is by being positioned at the end of outlet plenum 612 Outlet 612 leave pump.Power needed for mobile plunger is provided by the moment of torsion being input in axle 506 (seeing Fig. 9).This moment of torsion Being transferred to pivotal pin 534 (seeing Fig. 9), at pivotal pin 534s, this moment of torsion is transferred to swash plate 508 subsequently.

It is attached with rotary valve 514 and rotary valve 514 in the end relative with spline 532 of axle 506 via c clevis 512 are held in place.Whenever axle 506 rotates, rotary valve 514 rotates with identical rotary speed.Similarly, swash plate 508 is via pin 534 are connected to axle 506 between two ends of axle 506.Whenever axle 506 rotates, swash plate 508 is with the speed identical with axle 506 Rotate.Axle 506 transferring element that rotates, is because that axle 506 receives the rotary motion from external motors, finally makes rotation Rotary valve 514 and swash plate 508 rotate, thus produce pumping force.

Alternatively, axle 506 receives the rotary motion from swash plate, and the rotary motion of swash plate is from by the stream of rotary valve Body, this is converted into rotate the rotary motion (i.e. so that pump is used as motor in turn) of spline 532.In order to make flowing anti- To (alternatively, hereinafter referred to as " changing center (going over center) "), it is necessary to valve with passage current location Add extra interconnection on contrary sidepiece.It the reason that add extra interconnection is owing to high pressure interconnection becomes Low pressure, and low pressure interconnection becomes high pressure.

With reference to Figure 12, swash plate 508 is attached to axle 506 via pin 534.Pin 534 in axle 506 allows swash plate 508 to tilt, from And make the axis change relative to axle 506 for the axis of swash plate 508.It is extended with hollow stem 554 from the basal surface of swash plate 508.With axle 506 pins 534 engaging are positioned in this bar 554.In addition to being extended with bar 554 from swash plate 508, the basal surface of swash plate 508 is Smooth.Bottom the flat bottom of this flat surfaces permission swash plate 508 of swash plate 508 and piston shoes, the slip between 526 is mutual Effect, this is illustrating in greater detail below.

Pin 534 contributes to the rotation of the axis around axle 506 for the swash plate 508.Pin 534 is arranged for making moment of torsion and thrust load Transmit between swash plate 508 and axle 506.The advantage of pin 534 there are provided single type swash plate, thus owing to acting on swash plate Power on the two opposite sides of 508 and the stability that provides structure.

In pump previously, employ rotary cylinder-block.Therefore, it is necessary to use bolt to keep housing to cylinder body.Axially The housing of pump is the combination of two parts, and wherein, pump is kept together by all bolts.Need to suppress dividing of multiple piston zone From power, and pass through the design, it is thus only necessary to consider the power (due to single type housing) that the weight of parts and bearing apply.Such Advantage is: do not act on bolt due to tensile force, and therefore bolt has the longer life-span.In addition, it will require use close Sealing maintain the junction surface between cylinder body and housing in hydraulic fluid.

Radial load on pump is limited by limiting the inclination of swash plate.By less angle of inclination, have less Lateral load or moment (less radial load).It therefore reduces the importance of journal bearing and can use compared with underloading Bearing.Additionally, this pump allows the stroke reducing.Plunger is shorter but wider than conventional plunger than conventional plunger.Therefore, this pump leads to Cross the cubical content that the swash plate angle of inclination reducing just can be identical with conventional pump discharge.Cylinder body and pump case are one.Tool The reciprocating pump having fixing cylinder body has structural advantage.By removing the rotation of cylinder body, centripetal force is eliminated and has and subtracts The construction unit of little size and quality is possible.

Further, since swash plate has less angle of inclination, (for the operation of this pump, angle of inclination is not greater than about 12 degree It is necessary), can have the hole/diameter of plunger of increase without causing the reduction of volume flow.The diameter increasing and reduction Swash plate angle of inclination cause major part load be axial rather than radial direction.This achieve less friction on plunger and Abrasion, and then produce higher mechanical efficiency.The moment that a series of bearings 542 are intended to adapt to around the axis vertical with pin 534 carries Lotus.Bearing 542 is above and below the central point of pivotal pin 534, to balance the high-pressure side of swash plate 508 and low-pressure side.

The center of the tilt axis of swash plate and piston shoes bulb 528 is consistent with same plane, the cunning of this plane and swash plate 508 Dynamic face is parallel.This configuration limits the size in 526 paths advanced along the sliding surface of swash plate 508 bottom piston shoes.

Lemniscate is similar to the shape of infinity-sign, and lemniscate also can describe such as Fig. 8.Bottom this shape representation piston shoes 526 paths advanced with regard to the lower surface of wobbler 508 during shifting.In addition to lemniscate path, bottom piston shoes 526 Also advance 360 deg (more accurately, swash plate is with regard to 526 rotating 360 degrees bottom non-rotating piston shoes) with regard to swash plate 508.Effectively Ground, when swash plate 508 rotates, bottom piston shoes, 526 inwardly and move radially outward.During this rotation, piston shoes pressure chamber 550 (figure Shown in 12 and Figure 13) in fluid constantly sheared.

The flat bottom surface with swash plate 508 pressing chamber 550 to be centered in boots portion bottom piston shoes bottom each piston shoes contacts On flat surfaces.Bottom each corresponding piston shoes press chamber 550 be connected to fluid supply unit, with ensure boots portion/swash plate interface in Fluid pressure at the head of existing fluid pressure and each plunger 522 matches all the time.

With reference to Figure 13, piston shoes bulb 528 engages with plunger 522 in piston shoes bulb receiving portion 544.Due to piston shoes bulb In 528 holes 546 that can essentially enter into plunger, therefore piston shoes bulb 528 can limit the length of plunger 522, and then limit System is in the exposed surface (length) of fully extended plunger 522, and then reduces undesired torque load.Behaviour at pump 522 During work, the axially-movable of plunger 522 is transferred to piston shoes bulb 528.Piston shoes bulb 528 is also around its central rotation and therefore produce Give birth to transverse movement and make a concerted effort.Cross force causes the undesired moment around the axis orthogonal with the rotation of axle.In order to reduce This moment, the transverse movement (with making a concerted effort) in piston shoes bulb is reduced.Reduce transverse movement and a mode of power is to reduce post Plug 522 such as stroke described elsewhere herein.

Swash plate 508 rotates with the axis, but slippery boots assembly 514 does not rotates with the axis.Bottom swash plate 508 and piston shoes between 526 There is fluid film supporting member 576.Although the gradient of 526 constantly changes bottom piston shoes, but 526 still maintain and non-rotation bottom piston shoes Rotary column plug 522 and the alignment in hole 546.Owing to so, bottom piston shoes, 526 receive in recess 572 along lemniscate at its piston shoes bulb Path is moved.Bottom piston shoes, the path around the following side of swash plate 508 of 526 is oval (not being annular).Additionally, only piston shoes With pressure strip nutating (that is, the axis vibrating or tilting of axis is with regard to the rotation of central axis).

Pressure strip 510 keeps slippery boots assembly 524 in place against swash plate 508.Pressure strip 510 is by being fixedly engaged swash plate A series of bearings 542 of 508 are held in place on swash plate 508.In order to be assembled on swash plate 508 pressure strip 510, pressure strip 510 in the central portion in there is through hole.Swash plate 508 slides through the centre bore of pressure strip 510 and a series of bearing 542 tiltedly Slide on dish 508.

Pressure strip 510 is provided with multiple opening, and each opening in the plurality of opening is around corresponding slippery boots assembly 524 Neck 530.Corresponding special washer 578 be fixed into piston shoes bottom 526 integral.Each packing ring 578 makes piston shoes via stream Body supporting member 576 remains with the flat bottom surface of swash plate 508 and contacts.Pressure strip 510 is prevented from independent of bottom piston shoes 526 And rotate, and pressure strip 510 does not limit the motion of bottom piston shoes 526 simultaneously.Pressure strip 510 make bottom piston shoes 526 keep with tiltedly Dish 508 flushes, thus maintains the pressure between 526 and swash plate 508 bottom piston shoes.

The angle of swash plate 508 is adjusted by pumping fluid in one of two capacity portions 582 and 584 capacity portion Joint.Fluid is pumped in the first capacity portion 582 from external source to raise mobile plunger 580 or to be pumped into the second capacity portion To reduce mobile plunger 580 in 584.Mobile plunger 580 be hydraulically actuated with on axle 506 up and down, thus change swash plate 508 Angle.The displacement of mobile plunger is externally controlled.Hydraulic control is realized by outside hydraulic control (not shown). The displacement of mobile plunger 580 realizes the angular displacement of swash plate, and this realizes the displacement of plunger 522, thus produces fluid displacement.

With further reference to Figure 13, the through hole 573 that hydraulic fluid is allowed in piston shoes bulb 528 enters presses bottom piston shoes Chamber 550.The hydraulic fluid seal acting on 526 interactions with the flat surfaces of swash plate 508 bottom piston shoes and supporting Both parts.Neck 530 is connected to piston shoes bulb 528 by bottom piston shoes 526.Piston shoes neck 530 has through hole 574, and through hole 574 is The extendible portion of the through hole 573 of piston shoes bulb 528.Piston shoes bulb fluid inlet portion 572 and plunger through hole 571 continual communication, with The high-pressure fluid being pumped by plunger 522 is enable to enter.To this end, in view of the lasting rotation of piston shoes bulb 528, fluid inlet portion 572 are preferably taper.

With reference to Figure 14, the embodiment of rotary valve 514 is two-piece type assembly: thrust plate 600 and valve body 601 pass through screw 552 (shown in Fig. 9), adhesive or arbitrarily other securing members being suitable for keep together.Thrust plate 600 is together with valve body 601 As a valve 514.Thrust plate 600 is carried through the thrust load that axle 506 produces and carries.Axle 506 only passes through torque member Drive rotary valve 514.Axle 506 and rotary valve 514 are independently matched with to realize the moment of torsion of valve or rotary motion.Rotary valve 514 includes Entrance 602 (Fig. 9), passing away 616 and balance recess 606a and 606b.Balance recess 606a and 606b is configured to receive liquid Pressure fluid so that when rotating when axle 6 and rotary valve 514 and vibrate when plunger 522, the moment being caused by the motion of these parts It is balanced by the pressure in balance recess 606a and 606b.The bending table being positioned at rotary valve straight at passing away 616 It is provided with precompressed recess 620 in leading edge on face.This precompressed recess 620 is arranged to reduce by passing away 616 Quick increase of pressure and the damage of valve that causes.Precompressed recess provides the speed increasing the pressure in each pumping chamber Control, this control make on plunger produce impulsive force minimize.Minimized by making the impulsive force on plunger, bottom piston shoes It is minimized with the adjoint noise that is that cause and that be finally radiated local environment that contacts between swash plate.

Thrust plate 600 is positioned in the upper part relative with access road 602 of rotary valve 514.The surface of thrust plate 600 Area is equal to the half of the total surface area of plunger (because at any time the half of the total surface area of plunger will be at high pressure Under).The major obstacle of any axial plunger pump is to process bigger thrust load, and this thrust load is by from plunger hole 546 The lasting movement on plunger high pressure produce.Half plunger in plunger will have a high-pressure spray, and second half plunger To have lowpressure stream, this depends on position in hole for the plunger.Lubrication occurs under high pressure or low pressure.Load passes from plunger 522 It is handed to bottom piston shoes the 526th, to be transferred to swash plate and the 508th, is transferred to pivot pin 534, and be finally transferred to axle 506.Thrust plate 600 is used for Offset thrust load, axle 506 otherwise will be forced away from cylinder body 516.

Owing to be enough to resist less inlet pressure level along the film-strength on the surface of rotary valve, therefore need not be at rotary valve On low pressure recess is set.Additionally, add extra interconnection will cause too big fluid loss.

As observed in Figure 11 A and Figure 11 B, the recess in rotary valve 514 and cylinder bore 546 form an appearance Amount portion.Therefore, pressure is all equal in whole capacity portion.Recess 606a and 606b contributes to offsetting by around multiple plungers The pressure of 522 rotates the moment causing.Plunger 522 does not rotate around the axis of axle 506, but, plunger 522 is in its respective hole Reciprocating motion in 546 causes the moment with regard to the axis vertical with the axis of axle 506.Recess also allows for access road 536 edge The axis (axis with pump) rotary valve centers.Owing to being non-rotary plunger, therefore centripetal force is eliminated.Therefore, rotate Valve 514 is by using the hydrodynamic balance of the formula that is interconnected and automatically self centering.

Recess 606a and 606b of Figure 11 A to Figure 11 B represents the region with high pressure, and entrance 602 represents low pressure.Entrance Pressure near atmospheric condition, unless be additionally configured to pressure.Outlet pressure can reach 6000psi and higher.Two Recess 606a and 606b is separated by high-pressure outlet passage 612.Recess 606a is bigger than recess 606b, with balance with regard to rotation The moment of the vertical axis of shaft axis.Surface long enough between passage 606a and passage 606b, to guarantee valve in its hole Suitable sealing.The length of each passage in passage 606a and 606b is based on fluid pressure.Below equilibrium is used for determining 606a Ratio with 606b.

The capacity part of the full fluid that hydrodynamic thrust bearing member 610 is between thrust plate 600 and clack box 518.

The projected area of high-pressure outlet 612 and valve passing away 616 is equal dimensionally, thus balances therein Cross force on rotary valve 514.Additionally, these areas positioning is on the y axis so that with regard to the moment of barycenter be zero.It is positioned at The thrust bearing of the upper end of pump can process the value area that a plunger is in operation pressure.

The entrance stream of rotary valve passes through the central portion of valve along the axis (and therefore and along the axis of pump 502) of valve The outlet stream of access road 602 and rotary valve 514 is discharged at the adjacent peripheral edges of pump framework.The position of outlet 612 has additional Benefit: it contributes to cooling pump 502.Allow to lead to plunger hole 546 through the access road 602 of the central portion of rotary valve 514 More direct flow path.Owing to access road 602 provides more direct flow path and relatively low surface area, therefore Which also reduces the volume of suction chamber, also reduce fluid friction and thus reduce supplementary loss.

Plunger housing and discharge chamber (clack box) are combined into a unit (parts) by this pump 502.By combining high pressure In a housing, the power of the separation generally occurring within the pump of prior art is eliminated.In the balance not needing rotary valve 514 In the case of effect, valve will fall over or tilt, and may destroy fluid barriers, and may block the rotary part of pump 502. By this power, valve will look for the center of self in its hole.

Implementation below is intended to avoid the abrasion 698 as shown in Figure 15 on rotary valve.This abrasion is generally by valve Eccentric rotary in the valve opening of pump and upset cause.

Referring in particular to Figure 16, the first disclosed embodiment is the pump 702 of the clack box 706 including housing 704 and one. Rotary valve 708 is surrounded by clack box 706.Rotary valve 708 includes axle the 710th, section 712 with holes and seals section 714 (Figure 17 A extremely figure Shown in 17E).Seal section 714 and include semicircular sealing spine 716.Referring specifically to Figure 17 C, show across seal ridge The pressure drop in portion 716.As by shown in barometric gradient 740, pass through section with holes fluid relative to section with holes outside pressure Power is in compared with low pressure.

With reference to Figure 18 and Figure 19, rotary valve 708 includes the first axial face being positioned on the first end 720 of rotary valve 708 Seal 718 and the second axial face seal 722 being positioned on the second end 724 of rotary valve 708.High pressure discharges section 726 It is positioned on the sidepiece contrary with semicircular sealing spine 716 of rotary valve.Introduce section 728 and be positioned at the first of rotary valve 708 On end 720.

As shown in Figure 20, operating clearance 730 is positioned between high pressure discharge section 726 and clack box 706.Operating clearance 730 Width depend on discharging the power that the semicircle direction sealing spine at section 726 applies along being in high pressure.Hole with sealing The sidepiece that section 714 engages stands the pressure lower than the contrary sidepiece of valve.This is owing to the contrary sidepiece of valve stands to come The pressure greatly being raised discharged from cylinder body in pump for the fluid.Owing to the higher pressure discharging sidepiece of valve is by valve court Promote to the hole of the low pressure side being positioned at valve, therefore seal section 714 and be maintained at away from clack box 706 basic in the whole life-span of pump At constant operating distance.No matter low pressure side (that is, sealing the sealing spine 716 of the section 714) loss of valve is how many, the row of valve Valve is always promoted by the higher pressure going out sidepiece towards hole so that seals section 714 and engages hole surface (via supporting member/stream Body supporting member/mechanical bearing etc.).Owing to so, the distance away from hole surface for the valve is always to maintain constant, even stand surface mill at valve Still keep constant during damage.The width of operating clearance additionally depends on the girth of axle rotating speed and valve.

Rotary valve 708 surrounds less than 306 for generally cylindrical and semicircular sealing spine 716 to rotary valve 708 Ten degree.Semicircular sealing spine 716 includes clack box bonding part 734 and recessed portion 736.Include for strengthening passage The flank 748 of 750.

Another disclosed embodiment is shown in Figure 21 to Figure 24.In Figure 21 and Figure 22 A, pump 800 has valve opening 802, valve opening 802 surrounds rotary valve 804.At least one axial face that rotary valve 804 has on the end being positioned at rotary valve 804 is close Sealing 806 and at least one the sagittal plane seal 808 being positioned on the curved surface of rotary valve 804.Operation sealed airspace 810 (Figure 24) it is positioned between sagittal plane seal 808 and valve opening 802.Operation sealed airspace 810 is protected during the operation of rotary valve 804 Hold the thickness being basically unchanged.

Delivery space 812 is positioned between rotary valve 804 and hole 802.Rotary valve 804 is in the direction of sagittal plane seal 808 On biased.This biasing is caused by the power being applied.The amount of the power being applied determines the width of operation sealed airspace 810.Executed The power adding is determined by the high-pressure fluid leaving pump 800 through valve 804.

Referring specifically to Figure 23, show across the pressure drop 836 sealing spine 716.As by that shown in barometric gradient 836 Sample, the pressure of the outside relative to passage section 820 for the fluid passing through access road 820 is in compared with low pressure.

Rotary valve 804 is all-in-one-piece and is made up of following two parts: passage section 830 and axle 814.Sagittal plane seals Part 808 have semicircular seal member 816 and with axle 814 almost coaxial.Channel part 830 in present embodiment and axle 814 is coaxial.Channel part 830 includes access road 820 and passing away 822 (Figure 22 B).Pump 800 will by access road 820 Fluid introduces and fluid enters plunger hole, and this plunger hole is as above for receiving post described in previous embodiment Plug, this plunger is also activated by wobbler as described above.Fluid passes through identical piston to enter pump than fluid When the much higher pressure of pressure be forced off pump.Passing away 822 in channel part 830 for the fluid leaves pump 800.? Each plunger by fluid towards passage section 830 promote when, passage section 830 rotates with axle 814 so that passing away 822 connects Receive the high-pressure fluid from plunger.High-pressure fluid is subsequently directed towards the outlet 832 of pump 800.

In another embodiment as shown in Figure 25 and Figure 26, pump 900 has rotary valve 906, liquid in valve opening 902 Press pump 900 includes clack box 936.Axle 904 is positioned at clack box and is attached to the flat surfaces of rotary valve 906 at distal portion 908s 910.With reference to Figure 26, inclined each other as the axis of axle of first axle 912 and the axis as the rotary valve of the second axis 914 Move so that axis 912 and axis 914 be not coaxial.Therefore, axle 904 and rotary valve 906 be connected to each other and static when, two At least one axis in axis is not coaxial with valve opening 902.

Second axis 914 is consistent with the axis 916 of valve opening 902.Sometimes, the axis 916 of the second axis 914 and valve opening 902 Coaxially, but, exist the axis 916 of the second axis 914 and valve opening 902 not exclusively coaxial when.In these times, the second axle The axis 916 of line 914 and valve opening due to they proximity, become the optimization of the possibility of coaxial and coaxial rotating and recognized For simply consistent rather than coaxial.

First axle 912 offsets from the center line 918 of clack box 936.Rotary valve 906 has high-pressure outlet 920.Axle 904 edge The direction skew contrary with the high-pressure outlet 920 of rotary valve 906.But, axle 904 can also be along the high pressure towards rotary valve 906 The direction skew of outlet 920.

Multiple cylinder bodies 926 in clack box 936 are arranged abreast and arrange and cloth in the way of in around the circle of valve opening 902 It is set to coaxial with valve opening 902.Rotary valve 906 and valve opening 902 almost coaxial.But, rotary valve 906 can not be same with valve opening 902 Axle.In addition, axle 904 can be all-in-one-piece with rotary valve 906, but this is not required for.

Axle 904 includes clack box contact surface 922.Bearing 924 is positioned in clack box 936 and contacts with axle 904.Work as axle 904 when offseting along the direction away from high-pressure outlet 920, flowing by the pressure fluid of high-pressure outlet 920 by the of rotary valve 906 Two axis 914 advance towards the axis 916 of valve opening 902.Therefore, rotary valve 906 contributes in view of flowing from the skew of axle 904 By the high-pressure fluid of rotary valve 906, and hence help to eliminate any bias thus causing.

Alternatively, axle 904 is made to move away from high-pressure outlet 920 and order about rotary valve away from high-pressure outlet 920.This helps It is the sidepiece contrary with high-pressure outlet 920 and the valve opening 902 of valve in this low-pressure side of low-pressure side guaranteeing rotary valve 906 Between sealing.

Figure 27 shows the part including valve 1002 in hole 1004 of hydraulic pump 1000.Sagittal plane seal 1006 On the radial surface 1008 of valve 1002 and be positioned between valve 1002 and hole 1004.Sagittal plane seal 1006 is at least part of Ground surrounds valve 1002.Seal spine 1010 to be positioned on the periphery of sagittal plane seal 1006.And passage 1024 is positioned at along footpath Midway distance to the height of face seal 1006.

Seal spine 1010 to highlight from sagittal plane seal 1006 towards hole 1004.Seal between spine 1010 and hole 1004 The gap of minimum dimension allow to form fluid bearing part between spine 1010 and hole 1004 sealing.Fluid bearing part is arranged to be used In rotation more stably in hole 1004 for the valve 1002.

Sagittal plane seal 1006 be C-shaped to be equipped with coaxially with valve 1002.As shown in Figure 32, seal at sagittal plane It is provided with O-ring 1048 between part 1006 and valve 1002.O-ring 1048 is typically oval, to surround passage 750.Permissible The otch 1050 (or cutting out the otch for other O-ring any Anywhere at other) for O-ring is cut out in valve, but This is not necessarily.Referring additionally to Figure 17 C, exist from recessed portion 734 towards the pressure drop of passage section 712, wherein, channel part Section 712 is similar with the passage 1024 of embodiment as shown in Figure 29, recessed portion 734 and the sagittal plane in present embodiment The part being positioned at the above and or below sealing spine 1010 of seal is similar to.This is to pass through phase owing to entering the fluid of pump The passage 1024 being partially in low pressure sagittal plane seal being positioned to the above and or below sealing spine 1010 enters Enter.Seal the top edge of spine 1010 and lower edge in bigger than the pressure closest to the part in hole sealing spine 1010 Under pressure.Additionally, as in selected previous embodiment, the higher pressure discharged on sidepiece of valve 1002 is by valve 1002 On the low pressure side be positioned at valve 1002 i.e., the hole 1004 sealing on spine's sidepiece being positioned at valve 1002 promotes. Sagittal plane seal 1006 is generally promoted by high pressure sidepiece towards hole 1004 so that seal spine 1010 engage hole surface (via Supporting member/fluid bearing part/mechanical axis bearing member etc.).Seal spine 1010 passage 1024 is surrounded completely so that passage is shielded To prevent the pressure reduction in pump as much as possible.

Sagittal plane seal 1006 (is referred to as " moment of torsion transmission alternatively via at least one sagittal plane seal pin 1016 Part ") it is connected to valve 1002.Each sagittal plane seal 1006 biases away from valve 1002 via sagittal plane seal spring 1018. Revolving force is transferred to rotary face seal 1006 from valve 1002 by torque transfer member 1016.Torque transfer member can be will to turn round Square is transferred to the pin of another parts, the high friction surface of projection, such as O-ring etc or any other dresses from parts Put.One of purpose due to sagittal plane seal 1006 is to provide for sealing the sealing ridden between splenium 1010 and hole 1004, Therefore sagittal plane seal 1006 is biased towards hole 1004 so that no matter pump operates under without pressure reduction or no matter pump is not Operating, seals and is all kept.Each sagittal plane seal pin 1016 rests upon in the recess 1036 of valve 1002 and each radial direction Face seal spring 1018 and pin almost coaxial and rest upon on shoulder 1038.

Axial face seal 1012 is positioned on the axial surface 1014 of valve 1002.Axial face seal 1012 is positioned at the axle of valve Between the axial surface 1015 in surface 1014 and hole 1004.Spine 1017 is via the axial surface 1015 of fluid bearing part and hole Contact.Axial face seal 1012 is also connected to valve 1002 via at least one axial face seal pin 1020.Close with axial face The second axial face seal 1026 that sealing 1012 is similarly constructed is positioned at the second axial surface 1003 of valve 1002.Second axle To carry out via the spine contacting with hole as contacted with axial surface 1015 to the sealing on surface.

Each axial face seal 1012 biases away from valve 1002 via axial face seal spring 1022.As schemed Observe in 27 and Figure 28, between sagittal plane seal 1006 and radial surface 1008 and axial face seal 1012 with It is provided with O-ring 1030 between axle.And as observed in Figure 29, seal spine 1010 and there is passage 1024, logical Road 1024 is oval through hole, and this through hole provides the fluid intake leading to valve 1002.O-ring 1030 provides radial seal And the static sealing between valve, simultaneously still provides sealing when allowing the little radial motion between both parts.Axial face Seal 1012 provides similar sealing via O-ring, simultaneously while allowing the motion between axial face seal and valve Sealing is still provided.

Figure 30 shows two-sided hydraulic pump 1100.Hydraulic pump 1100 includes swash plate 1102, and swash plate 1102 has the first sidepiece 1104 and second sidepiece 1106.First sidepiece of swash plate 1104 and the second sidepiece 1106 are substantially parallel.

The Part I 1108 of pump is positioned on the first sidepiece 1104 of swash plate.And the Part II 1110 of pump is positioned at swash plate The second sidepiece 1106 on.Part I 1108 has Part I rotary valve 1112 and Part I rotary valve by first Point hole 1114 surrounds.And Part II 1110 has Part II valve 1116 and Part II valve by Part II hole 1118 Surround.The two valve has axle 1120a, 1120b and radial seal 1126a, 1126b.Each radial seal has sealing Spine 1124a, 1124b and with the channel part being positioned at corresponding passage 1125a, 1125b connection the 1112nd, in 1116 for the corresponding valve Section 1122a, 1122b.

Part the 1108th, at least one part in 1110 have be connected to corresponding valve the 1112nd, 1116 corresponding radially Face seal 1126a, 1126b, sagittal plane seal 1126a, 1126b provide corresponding valve the 1112nd, 1116 with corresponding hole 1114th, the sealing between 1118.Torque transfer member 1128 is by corresponding sagittal plane seal 1126a, 1126b and corresponding valve 1112nd, 1116 connect, so that the 1112nd, 1116 revolving force is transferred to corresponding sagittal plane seal 1126a, 1126b from valve.In footpath It is provided with O-ring 1034a, 1034b between face seal 1126a.

Pass through the fluid stream of this pump to seal other parts by pump, axial face seal 1026 should be positioned at valve The contrary sidepiece of the opposite segments with valve on.As observed in Figure 31, sagittal plane seal 1006 suffers pressure Gradient.Barometric gradient is the pressure by the fluid being forced in valve by plunger in cylinder body 1042 for the higher pressure section 1040 The result applying to valve 1002.Pressure ratio sagittal plane seal at the lateral end portions 1044 of sagittal plane seal 1006 Pressure at the mid portion 1046 of 1006 is high.

Foregoing disclose is described as pump.But, those of ordinary skill in the art it will be appreciated that, disclosed dress Put and can serve as hydraulic motor, fluid power motor etc..

Although being described previously is considered as optimal pattern and/or other examples, it is understood that, permissible Make various remodeling and presently disclosed subject matter can be implemented with example in a variety of manners, and teaching can be applied In many application, only describe some application in described application herein.Claims are intended to requirement and fall and teach at this Any and all application, remodeling and modification in actual range.

Claims

1. a plunger assembly, comprising:

Static cylinder body,

Axle, described axle can rotate in described static cylinder body around the axis of himself, and described axle includes multiple passage, The plurality of passage is configured to receive, guides and exhaust fluid, and described axle can medially and prejudicially during the operation of pump Rotate, and

Swash plate, described swash plate is attached to described axle, and described swash plate has the first sidepiece, and described first sidepiece couples multiple first Plunger.

2. plunger assembly according to claim 1, wherein, described swash plate is configured to hang down with regard to the described axis with described axle Straight axis tilts.

3. plunger assembly according to claim 2, also includes the device for making described swash plate tilt.

4. plunger assembly according to claim 1, wherein, the fluid pressure on described passage in described axle makes at least one Individual power and/or equalising torque.

5. plunger assembly according to claim 1, also includes bottom multiple corresponding piston shoes, the plurality of corresponding piston shoes Bottom is each attached to plunger, and described swash plate include for described piston shoes bottom at least one effect table of interacting Face.

6. plunger assembly according to claim 1, wherein, the fluid stream running through described pump produces power and power on the shaft At least one and the plurality of passage in square constructs on the shaft so that in described power on described axle or described moment Described at least one be balanced.

7. plunger assembly according to claim 6, also includes multiple second plunger, the plurality of first plunger and described many It in individual second plunger is respectively received in described cylinder body and is positioned and described axle on relative two end of described cylinder body In coaxial arch.

8. plunger assembly according to claim 7, also includes the first action face and the second action face, and described first makees It is positioned on contrary two sidepiece of described swash plate by surface and described second action face.

9. a plunger assembly, comprising:

Static cylinder body；

Axle, described axle extends through described static cylinder body and has a part of multiple passage along described axle；And

Valve, described valve closure is in described static cylinder body, and described valve includes the described axle being integrally coupled to described valve.

10. plunger assembly according to claim 9, also includes multiple first plunger and multiple second plunger, the plurality of First plunger and the plurality of second plunger are positioned with coaxial with described axle respectively on relative two sidepiece of described axle Arch on.

11. plunger assemblies according to claim 9, wherein, the plurality of passage is configured to receive, guide and discharge run through The fluid stream of pump.

12. plunger assemblies according to claim 11, wherein, the described fluid stream running through described pump produces on the shaft At least one in multiple power and multiple moment, and the plurality of passage construction make the plurality of power and institute on the shaft State in multiple moment described at least one be balanced.

13. plunger assemblies according to claim 12, also include:

Multiple slippery boots assemblies, each slippery boots assembly is both coupled to one of the plurality of plunger plunger；And

Swash plate, described swash plate is attached to described axle and described swash plate includes for interacting extremely with corresponding slippery boots assembly A few action face.

14. plunger assemblies according to claim 13, also include the first action face and the second action face, described first Action face and described second action face are positioned on contrary two sidepiece of described swash plate.

15. 1 kinds of plunger assemblies, comprising:

Swash plate, described swash plate has the first sidepiece and the second sidepiece, and described first sidepiece couples to be had bottom multiple first piston shoes, institute Stating the second sidepiece connection has bottom multiple second piston shoes, described first sidepiece of described swash plate and described second side of described swash plate Portion is substantially parallel；And

Part I on described first sidepiece being positioned at described swash plate of pump and described pump be positioned at described the of described swash plate Part II on two sidepieces, the described Part I on described first sidepiece being positioned at described swash plate of described pump and described pump Described Part II with regard to described swash plate almost symmetry.

16. plunger assemblies according to claim 15, also include axle, and described swash plate is attached to described axle.

17. plunger assemblies according to claim 16, are constructed to be permeable to tilt with respect to the axis of described axle or hang down Straight axis is adjusted.

18. plunger assemblies according to claim 16, also include for making effect multiple power on the shaft and multiple The device of at least one balance in moment.

19. plunger assemblies according to claim 17, also include the dress for making described swash plate tilt relative to described axle Put.

20. plunger assemblies according to claim 16, also include around described axle, described swash plate and described slippery boots assembly Housing.

21. 1 kinds of plunger assemblies, comprising:

Static cylinder body,

Valve-shaft assembly, described valve-shaft assembly is surrounded by described static cylinder body, and described valve-shaft assembly includes valve and axle, described Interaction between valve key groove in driving key and described valve for the valve and the shaft key groove in described axle and be connected to described The described axle of valve-shaft assembly, and wherein, described interaction is constructed at least one of the relatively described axle of described valve offer The free degree.

22. plunger assemblies according to claim 21, wherein, described valve is configured to according in the power on described valve and moment At least one by check leak rate in hydraulic pump for the fluid and in described cylinder body inner equilibrium.

23. plunger assemblies according to claim 22, also include the swash plate being connected to described axle.

24. plunger assemblies according to claim 23, also include for making described swash plate hang down with regard to the axis with described axle The device that straight axis tilts.

25. plunger assemblies according to claim 24, wherein, described swash plate includes at least one action face.

26. plunger assemblies according to claim 25, wherein, described swash plate includes multiple slippery boots assembly, the plurality of cunning Boots assembly is attached at least one action face described of described swash plate.

27. 1 kinds of plunger assemblies, comprising:

Housing and with described housing all-in-one-piece clack box, and

Rotary valve, described rotary valve is surrounded by described clack box, and described rotary valve includes axle, passage section and seals section,

Wherein, described sealing section includes semicircular sealing spine.

28. plunger assemblies according to claim 27, described rotary valve also includes the first axial face seal and the second axle To face seal, described first axial face seal is positioned on the first end of described rotary valve, described second axial face seal Part is positioned on the second end of described rotary valve.

29. plunger assemblies according to claim 28, described rotary valve also include being positioned at described rotary valve with described half The circular high pressure sealing on the contrary sidepiece of spine discharges section.

30. plunger assemblies according to claim 29, described rotary valve also includes be positioned at described rotary valve described first Introducing section on end.

31. plunger assemblies according to claim 29, also include being formed at described high pressure discharge section and described clack box it Between operating clearance, the width of described operating clearance depend on described high pressure discharge at section along described semicircular sealing The power that the direction of spine applies.

32. plunger assemblies according to claim 31, wherein, described semicircular seal ridge cage structure becomes to be maintained at away from institute State at the operating distance that clack box is basically unchanged.

33. plunger assemblies according to claim 31, wherein, the width of described operating clearance additionally depends on axle rotating speed and institute State the girth of valve.

34. plunger assemblies according to claim 27, wherein, described rotary valve is generally cylindrical and described semicircle Sealing spine 360 deg is surrounded less than to described rotary valve.

35. plunger assemblies according to claim 34, wherein, described semicircular sealing spine includes clack box bonding part And recessed portion.

36. plunger assemblies according to claim 28, described rotary valve also include being positioned at described rotary valve with described half The circular low pressure suction part sealing on the relative sidepiece of spine.

37. 1 kinds of plunger assemblies, comprising:

Valve opening,

Rotary valve, described rotary valve is surrounded by described valve opening, and described rotary valve includes at least one axial face seal and at least One sagittal plane seal,

Operation sealed airspace, described operation sealed airspace is positioned between described sagittal plane seal and described valve opening,

Wherein, described operation sealed airspace keeps the thickness being basically unchanged during the operation of described rotary valve.

38. plunger assemblies according to claim 37, also include being positioned between the discharge between described rotary valve and described hole Gap, described rotary valve is biased by the power applying along the direction of semicircular sealing spine, and wherein, described power determines described behaviour Make the width of sealed airspace.

39. plunger assemblies according to claim 38, described rotary valve also includes axle, wherein, described sagittal plane seal Including semicircular seal member and with regard to described axle almost coaxial.

40. plunger assemblies according to claim 39, also include the passage section being positioned on described axle.

41. plunger assemblies according to claim 40, wherein, described axle includes access road and passing away.

42. 1 kinds of plunger assemblies, comprising:

Housing, described housing has valve opening and clack box,

Axle and rotary valve, described axle is positioned at described clack box, and described rotary valve is positioned at described valve opening, and described axle is attached at far-end It is connected to the flat surfaces of described rotary valve；And

Described axle has first axle and described rotary valve has the second axis, and described first axle is inclined from described second axis Move.

43. plunger assemblies according to claim 42, wherein, the dead in line of described second axis and described valve opening.

44. plunger assemblies according to claim 43, wherein, described first axle is from the disalignment of described clack box.

45. plunger assemblies according to claim 42, wherein, described rotary valve includes high-pressure outlet.

46. plunger assemblies according to claim 45, wherein, described axle is along the side of the described high-pressure outlet of described rotary valve To skew.

47. plunger assemblies according to claim 46, wherein, described axle includes clack box contact surface.

48. plunger assemblies according to claim 45, wherein, described axle is along the described high-pressure outlet phase with described rotary valve Anti-direction skew.

49. plunger assemblies according to claim 42, also include the multiple cylinder bodies being positioned at described clack box, the plurality of cylinder Body is arranged and abreast around described valve opening and the circle arrangement coaxial with described valve opening.

50. plunger assemblies according to claim 49, wherein, described rotary valve and described valve opening almost coaxial.

51. plunger assemblies according to claim 50, wherein, described axle is not coaxial with described valve opening.

52. plunger assemblies according to claim 42, described axle is all-in-one-piece with described rotary valve.

53. 1 kinds of plunger assemblies, comprising:

Valve, described valve is positioned at hole,

Sagittal plane seal, described sagittal plane seal is positioned on the radial surface of described valve, is positioned at described valve and described hole Between and at least partially around described valve, described sagittal plane seal include seal spine, and

Axial face seal, described axial face seal is positioned on the axial surface of described valve, and described axial face seal is positioned at Between the described axial surface of described valve and the axial surface in described hole.

54. plunger assemblies according to claim 53, wherein, described sealing spine towards described hole away from the institute of described valve State radial surface to highlight.

55. plunger assemblies according to claim 53, wherein, described sagittal plane seal is close via at least one sagittal plane Sealing torque transmitter is connected to described valve.

56. plunger assemblies according to claim 55, wherein, described sagittal plane seal is close via at least one sagittal plane Sealing spring is biased away from described valve.

57. plunger assemblies according to claim 53, wherein, described axial face seal is close via at least one axial face Sealing torque transmitter is connected to described valve.

58. plunger assemblies according to claim 57, wherein, at least one described axial face seal is close via axial face Sealing spring is biased away from described valve.

59. plunger assemblies according to claim 53, wherein, described sealing spine also includes passage.

60. 1 kinds of plunger assemblies, comprising:

Swash plate, described swash plate has the first sidepiece and the second sidepiece, and described first sidepiece is almost parallel with described second sidepiece；

The Part I of pump and Part II, described Part I is positioned on described first sidepiece, and described Part II is positioned at institute State on the second sidepiece,

Described Part I includes the Part I rotary valve being surrounded by Part I hole, and described Part II includes by The Part II valve that two partial hole are surrounded,

Wherein, two valves all include axle, passage section and seal spine.

61. plunger assemblies according to claim 60, wherein, at least one part in described part also includes being connected to Corresponding valve and corresponding sagittal plane seal that sealing between corresponding described valve with corresponding described hole is provided.

62. plunger assemblies according to claim 61, also include connecting corresponding sagittal plane seal with corresponding valve So that revolving force to be transferred to from valve the torque transfer member of corresponding sagittal plane seal.