CN105089961A - Hydrostatic piston machine - Google Patents
Hydrostatic piston machine Download PDFInfo
- Publication number
- CN105089961A CN105089961A CN201510222194.4A CN201510222194A CN105089961A CN 105089961 A CN105089961 A CN 105089961A CN 201510222194 A CN201510222194 A CN 201510222194A CN 105089961 A CN105089961 A CN 105089961A
- Authority
- CN
- China
- Prior art keywords
- pressure
- piston machine
- control opening
- control piece
- voltage control
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
- F04B1/22—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block having two or more sets of cylinders or pistons
- F04B1/24—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block having two or more sets of cylinders or pistons inclined to the main shaft axis
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
- F03C1/00—Reciprocating-piston liquid engines
- F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
- F03C1/06—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis
- F03C1/0636—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
- F03C1/0644—Component parts
- F03C1/0647—Particularities in the contacting area between cylinder barrel and valve plate
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
- F04B1/2014—Details or component parts
- F04B1/2021—Details or component parts characterised by the contact area between cylinder barrel and valve plate
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Reciprocating Pumps (AREA)
Abstract
The invention relates to a hydrostatic piston machine having a housing for accommodating return oil, a rotary cylinder body leaning against a control member and having a plurality of cylinder chambers. A piston in the piston machine passes a cylinder chamber afflux part and is alternately connected to a low pressure channel through a low pressure control opening of the control member and connected to a high pressure channel through a high pressure control opening. Two switching regions exist between the low and high pressure control openings on the control member. The piston reverses a motion direction in a dead point, and the corresponding cylinder chamber afflux part sweeps the switching regions of the control member. A pre-control opening exists in the switching regions. The cylinder chamber afflux part switches from the high pressure control opening towards the low pressure control opening of the control member. Before the cylinder chamber afflux part is opened to the low pressure control opening, the cylinder chamber afflux part is connected a low pressure region through a pressure reduction flow path with a first throttling device. The pressure reduction flow path is configured to be pressure reduction cascade. Besides the first throttling device, the pressure reduction flow path has at least a second throttling device in serial connection with the device and has a flow container between the two serial devices.
Description
Technical field
The present invention relates to a kind of as described in the preamble hydrostatic piston machine according to Patent right requirement 1, especially a kind of hydrostatic axial piston machine.Axial piston machine in especially a kind of clino-axis type mode of structure of hydrostatic axial piston machine and be especially applied as pump.
Background technique
The hydrostatic piston machine of type belonging to a kind of is such as open in EP953767B1.Hydrostatic piston machine like this has low-pressure channel and high-pressure channel, and they construct in the connecting plate of main casing or shell.The inside of shell is completely or partially filled with oil return at work.Hydrostatic piston machine also has the cylinder body of rotation, described cylinder body to rest on control piece and has multiple cylinder room, in described cylinder room, be provided with the piston operationally implementing stroke motion, and wherein each piston can be connected by remittance portion, cylinder room and be connected with high-pressure channel by the high voltage control opening of control piece in an alternating fashion with low-pressure channel by the low voltage control opening of control piece.That stroke motion along with piston changes, between piston and control piece volume freely can be described as active chamber.On control piece, between low voltage control opening and high voltage control opening, existence two is Zone switched.Piston is turned back its moving direction in dead point, and the inswept control piece in corresponding remittance portion, cylinder room is Zone switched.Pre-control opening is there is in Zone switched, low voltage control opening conversion in remittance portion, described Zone switched middle cylinder room from high voltage control opening towards control piece, remittance portion, described cylinder room was connected with area of low pressure via the pressure reducing fluid path with first throttle device by described pre-control opening before it is opened to low voltage control opening.
Should the high pressure that dominate in active chamber after inswept high voltage control opening be slowly reduced on lower pressure by pressure reducing fluid path, thus when active chamber is opened to low voltage control opening by remittance portion, corresponding cylinder room, the pressure in active chamber and the difference between the pressure in low voltage control opening reduce or are zero.Can affect the noise emissions of piston machine and mechanical loaded favourable thus.
Concerning known hydrostatic piston machine, be connected to the valve that can adjust in proportion before throttling arrangement, by opening of the growth of described valve, first propping up the high pressure fitted in active chamber should little by little reduce.It is at least that requirement is very harsh that and frequency that utilization necessary higher to the input of extra valve controls described valve.
Concerning hydrostatic piston machine, usually formed the pressure reducing fluid path not having valve by so-called pre-control groove, described pre-control groove be presented to turning in the side of described cylinder body of control piece and initial in the spacing in the front of low voltage control opening, finally import in described low voltage control opening to described its cross section of low voltage control enlarged open.The hydrostatic piston machine with such pre-control groove is such as known from US5230274A.
Concerning so common pressure reduces and switches, the high pressure in active chamber is reduced in the pressure fitted in low voltage control opening, such as ambient pressure level by pre-control groove.In this case, decompression oil flows out with very high speed, thus produces cavitation bubbles in shear zone, transition zone namely between the pressure fluid of static and quick flowing.Extraly, also the pressure fluid in described district is foamed.Because after pressure reduces, piston starts from intake stroke, then the possibility existed is, temporarily reduce switching by pressure and again draw.So piston can suction pressure fluids/gases/air mixture again.This causes the defective degree of filling of active chamber.
Therefore, reduce at pressure in the region switched and can occur cavitation corrosion.Raise in the region switched at pressure and occur cavitation corrosion equally, described pressure raises to switch and is usually also configured with the pre-control groove be connected on high voltage control opening, because the volume of pressure fluid/gaseous mixture must be filled to the more pressure fluid from high voltage control opening, therefore need more for constructing the pressure fluid of pressure.This higher demand to compressed fluid means, when constructing pressure, pressure fluid flows in active chamber and thus increase hole with high flowing velocity for a long time from high pressure.Finally, the incomplete degree of filling of active chamber causes suction in advance to be interrupted extraly.
Summary of the invention
Therefore the present invention for task be, so further develop the hydrostatic piston machine of the feature of the preamble with Patent right requirement 1, thus reduce the tendency in hole and thus prevention cavitation corrosion and improve the durability of component with simple means.
Described task solves with the hydrostatic piston machine with high-pressure channel by having low-pressure channel, it has the shell holding oil return, there is the cylinder body of rotation, described cylinder body setting and have multiple cylinder room on control piece, is provided with the piston implementing stroke motion at work in described cylinder room and wherein each piston can be connected with low-pressure channel by the low voltage control opening of control piece in an alternating fashion by remittance portion, cylinder room and be connected with high-pressure channel by the high voltage control opening of control piece.Control piece has between low voltage control opening and high voltage control opening two Zone switched, wherein its moving direction is reversed by piston in dead point, and the inswept control piece in corresponding remittance portion, cylinder room is Zone switched, and wherein in Zone switched, there is pre-control opening, low voltage control opening conversion in remittance portion, described Zone switched middle cylinder room from high voltage control opening towards control piece, remittance portion, described cylinder room was connected with area of low pressure via the pressure reducing fluid path with first throttle device by described pre-control opening before it is opened to low voltage control opening.Feature according to hydrostatic piston machine of the present invention is, pressure reducing fluid path configuration is the low cascade of Pressure Drop, and described decompression cascade also has at least one and is in the second throttling arrangement in connecting with first throttle device and is in each other at two between the throttling arrangement in series connection and have fluid container (Fluidkapazit t) except first throttle device.
Wherein concept " fluid container " the description chamber of filling with pressure medium, its volume compared to the common passage between two flow controllers volume obviously more greatly and wherein pressure change be associated with the inflow of pressure medium or outflow due to the compressibility of pressure medium.
Pressure Drop is rudimentary be associated in the simplest situation comprise form first throttle device first throttle device, form fluid container between the second choke of the second throttling arrangement and two flow controllers.When being reduced by the pressure of pressure reducing fluid path in active chamber, second choke hinders pressure reducing fluid to flow out in area of low pressure.In fluid container, improve pressure thus, thus the foaming of the appearance in hole and pressure fluid is avoided to a great extent.When piston starts to draw by the expansion of active chamber owing to reducing the locomotory mechanism switched on geometrical construction at a kind of pressure, then the hole likely occurred and air bubble no longer exist.In addition the high pressure in fluid container is assisted, and is expressed in active chamber by pressure fluid.
Relative to the simplest situation, can other fluid container and flow controller be utilized to expand low for Pressure Drop cascade.Therefore compare an only fluid container and can there is more fluid container, wherein before fluid container, between and correspondingly afterwards have throttling arrangement.
Major advantage of the present invention is from following, namely hydrostatic piston machine has long wear life, because the damage of constructing the component that the hole in region is caused due to pressure reduction and pressure is avoided, rotating speed is drawn and this is not when or only have when small extra cost and realize it is thus possible that improve.
According to the favourable remodeling of hydrostatic piston machine of the present invention in the dependent claims.
Concerning a kind of hydrostatic piston machine that can adjust in its stroke volume, dead volume changes along with the change of stroke volume.Wherein dead volume is the minimum volume of piston when a reversing of motion of piston and the active chamber between control piece.The quantity delivered of piston machine when stroke volume is each revolution of live axle or uptake.Larger compared to large stroke volume concerning dead volume little stroke volume.Stroke volume advantageously can be utilized now to be changed by the effective through flow cross section of throttling arrangement.Because the decompression for large dead volume must flow out the more decompressed pressure fluid of the decompression compared to little dead volume, thus the effective through flow cross section of the throttling arrangement paid close attention to when little stroke volume compared to larger during large stroke volume.
Described pressure reduces fluid path and can direct in the low voltage control opening of control piece or direct in low-pressure channel.
Certainly advantageously, described pressure reduction fluid path directs in the region of accommodation oil return of shell.So do not disturb the fluid in low-pressure channel or in low voltage control opening to flow.
Preferably constructed particularly by holing by the throttling arrangement in control piece, wherein first throttle device is formed by the hole of single minute diameter.
The present invention can be used in using for the hydrostatic piston machine with the constant stroke volume that maybe can adjust of pump and motor operations type.Piston machine can such as be configured to the axial piston machine of inclined disc type mode of structure or radial piston machine.
Especially advantageously, the present invention also realizes in a kind of hydrostatic piston machine being configured to clino-axis type machine, and described clino-axis type machine especially can adjust in its stroke volume.Such piston machine has driving flange on the driving shaft, and described driving flange hingedly supports piston.Control piece has the groove of central authorities, concerning the energy scalability of stroke volume, embeds the adjusting pin of regulating mechanism in described groove.In a kind of especially favourable remodeling, as long as described groove can't help adjusting pin or be full of by guide finger, then present described groove at least as the fluid container had in first throttle device downstream a part and be present in pressure and reduce in fluid path.The boring of control piece inside directly can be directed in the groove of central authorities from the pre-control opening the chain of command of cylinder body that turns to of control piece.Preferably described hole is not radially but tangentially directs in described groove on the edge of groove, thus liquid beam does not rush at the material of control piece.
Drop-center preferably in control piece and the gap between optionally truncated adjusting pin are the flow controllers belonging to the second throttling arrangement.More complicated relative to this, provide flow controller by the boring in adjusting pin.
Usually concerning with the hydrostatic piston machine of clino-axis type mode of structure, cylinder body has hole that is central, possibility classification, and contain the intermediate pin of guiding cylinder body in the hole, described intermediate pin hingedly supports on the driving flange of live axle.If the groove in the hole of the central authorities in cylinder body and control piece is opened each other, the hole of the central authorities so in cylinder body, the free volume of the groove of central authorities in the free volume of the volume of the possible cavity comprised in intermediate pin and control piece is jointly formed in the fluid container in first throttle device downstream.
When low pressure or shell pressure in the groove at control piece arrange, groove therefore substantially open wide to non-throttling towards area of low pressure and the second throttling arrangement above-mentioned does not exist in addition time, so from pre-control opening to the drop-center of control piece and to the hole of the central authorities may opened wide towards described groove of cylinder body fluid connect also can be favourable concerning the decompression of active chamber.Due to the excellent material behavior of control piece manufactured by tool steel under most cases, when there is no the second throttling arrangement, also damage can not caused by being flowing on control piece of pressure reducing fluid.Therefore original invention is therefrom also shown.
Concerning the especially preferred embodiment of one, guide a section of described pressure reduction fluid path by intermediate pin and when continuing guiding from here, guided a section in pressure reducing fluid path by live axle.Relative position between intermediate pin and the driving flange of live axle changes along with stroke volume.Advantageously so construct transition now, thus between these two sections from stroke volume about set different throttling cross sections.
Second throttling arrangement preferably by two mutually the parallel flow controllers arranged form, namely by the flow controller on the adjusting pin with constant through flow cross section with by the flow controller between intermediate pin and the driving flange with the through flow cross section changed along with stroke volume.
What pressure reduced fluid path directs in the leakage region of shell by the part of intermediate pin and live axle preferably by least one rolling bearing of live axle, and wherein rolling bearing is tapered roller bearing.Tapered roller bearing has certain pump efficiency fruit.
Accompanying drawing explanation
Multiple embodiments according to hydrostatic piston machine of the present invention schematically or particularly show in the accompanying drawings.By means of these accompanying drawings, specifically explain the present invention now.
Wherein:
The longitudinal cross-section of the first embodiment in total travel that Fig. 1 illustrates detail display, that be configured to clino-axis type machine;
Fig. 2 illustrates the longitudinal cross-section of the first embodiment in zero stroke;
Fig. 3 illustrates the plan view on the control side of the control piece of the first embodiment;
Fig. 4 is the explanatory view according to the embodiment of Fig. 1 to 3;
Fig. 5 is the explanatory view of the second embodiment, and wherein first throttle device and the second throttling arrangement are formed respectively by single flow controller;
Fig. 6 is the explanatory view of the 3rd embodiment, wherein by spring-loaded piston limit fluid container;
Fig. 7 is the explanatory view of the 4th embodiment, and wherein first throttle device is consisted of two flow controllers arranged that walk abreast mutually, and the second throttling arrangement is consisted of single flow controller, and
The longitudinal cross-section of the 5th embodiment in total travel that Fig. 8 illustrates detail display, that be configured to swash plate machine.
Embodiment
In Fig. 1 is to 3, first the hydrostatic axial piston machine in clino-axis type mode of structure of detail display is arranged for and utilizes the pump operation of hydraulic oil and have the shell 10 that the shell main part 11 comprising can-like is called for short the connecting plate 12 of shell tank and cover shell tank, described connecting plate constructs high pressure connecting end and low pressure, suction or storage tank connecting end and the shell simultaneously illustrated for regulating mechanism.In shell tank 11, can support live axle 16 rotationally by three tapered roller bearings 13,14 and 15, described live axle carries integratedly and drives flange 17.Supporting functions is met by two identical parallel tapered roller bearings 13 and 14 arranged mutually substantially.About two bearings 13 and 14 mirror image arrange, less tapered roller bearing 15 is for the reverse leading of live axle.
On driving flange 17, supported by spherical hinge and remain piston 18, described spherical hinge has the piston rod 19 and spherical piston head 20 that are configured to truncated cone, and described piston head slips in the hemispheric ball cap 21 driving flange 17, and described ball cap forms the second portion of corresponding spherical hinge.On driving flange 17, maintain piston 18 by the stagnant plate 22 that returns acted on from rear piston head 20, described time stagnant plate is tightened on driving flange 17.Piston 18 utilizes piston rod 19 to slip into and is also referred to as in axial piston machine in the cylinder room 29 unlimited to driving flange of the cylinder body 30 of cylinder barrel, and in cylinder room 29, limits active chamber 31 in this case, and its volume changes along with the stroke of piston.The side deviating from driving flange of cylinder barrel 30 exists remittance portion, cylinder room 32, and wherein each one imports passage guide cylinder room.Remittance portion, cylinder room is positioned on a pitch circle, and its radius is less than the joint radius of a circle having cylinder room, thus imports that passage is corresponding moves towards obliquely.Import the part that passage is active chamber in theory, because in described remittance passage, when piston operates back and forth, pressure medium is compressed and is reduced pressure, but can not be used to conveying, but forms the part of the dead volume of active chamber.
By driving flange 17 and piston 18, cylinder barrel is placed in rotation by live axle 16.The stroke of piston 18 adjusts according to the oblique angle of the axis 33 of cylinder barrel about the rotation axis 23 of live axle 16.Cylinder barrel 30 is guided by intermediate pin 35, described intermediate pin by slip into drive flange 17 ball cap 37 in and pass through back stagnant plate 22 within it and obtain firm bulb 36 and be hinged on driving flange on.On the other hand, intermediate pin 35 utilize columned axle slip into the central authorities of cylinder barrel 30, in the through hole 38 of classification.Described cylinder barrel 30 in the state do not loaded of pump only between intermediate pin and cylinder barrel the current spring do not specifically not illustrated of tensioning power under and extraly by the effect lower support of the pressure medium be under pressure to control piece 40 applied pressure in the state loaded, described control piece 40 is supported on the guide rail 41 of the column casing shape of connecting plate 12 in itself.The medial axis of guide rail 41 passes through the mid point of the bulb 36 of intermediate pin 35, thus when oblique angle changes, described intermediate pin and cylinder barrel do not move in the axial direction in opposite directions.
Relative to the oblique angle of axle axis 23 and therefore in order to the axis 33 that changes cylinder barrel is in order to the stroke volume of the stroke and pump that change piston 18, the end section 43 of ball-joint shape is utilized to embed adjusting pin 44 in groove 42 rounded in the cross section of through, central authorities, control piece 40, described adjusting pin is fixedly connected with regulating lever 45, and described regulating lever is placed in connecting plate movably.Adjusting pin and regulating lever are the parts of the regulating device of stroke volume for changing pump, and are tangential to guide rail 41 ground move to change stroke volume.When mobile, control piece 40 is passed and is changed the Angle Position of cylinder barrel relative to live axle thus on columned guide rail.
When the supporting surface 46 that the direction guiding rail 41 of control piece 40 turns to has columned profile corresponding to guide rail, so control the profile ball bumps ground structure of side 47.Construct to the corresponding spherical recess of supporting surface 48 of the chain of command 47 being opposed to control piece 40 of cylinder barrel 30.
In control side 47, control piece 40 has the high voltage control opening 58 of the kidney shape and the low voltage control opening 59 of the kidney shape, there is the storage tank pressure or low loading pressure that operational height is 5 bar at work within it current.Control to have so-called Zone switched 60 and 61 between opening at two, described Zone switched in, high pressure connecting end from low pressure connecting end to pump of the connection of active chamber and oppositely converting.In this case, pressure medium compresses or reduces pressure in active chamber.This should not occur on impact type ground because pump otherwise can very noisy and component can violent carrying.
Therefore for from low pressure to the switching of high pressure, the end of high voltage control opening is provided with extend in Zone switched 60, be the switching slot 62 of V-arrangement in cross-section, when low voltage control opening is left in remittance portion, cylinder room, first opened towards high voltage control opening 58 from remittance portion, cylinder room 32 by the little and cross-sectional flow expanded gradually by described switching slot.Wherein precondition is according to Fig. 3, cylinder barrel rotation along clockwise direction in the plan view of control piece.
Concerning the switching between high pressure and low pressure, in Zone switched 61, in the spacing in the front of low voltage control opening 59, with the smooth portion that mills out 63 for form exists pre-control opening, inclined hole 64 leads to the inside of control piece 40 from described pre-control opening.In inside, inclined hole 64 converges mutually with the hole 65 just tilted from the radial plane of control piece 40 slightly, and described hole 65 closes to the outside of control piece and tangentially imports in the groove 42 of the central authorities of control piece 40.
The supporting surface 48 of the immediately depression of cylinder barrel 40 of the through hole 38 in cylinder barrel 30 has a short section, and this section has a diameter, and described diameter is just slightly less than the diameter of the groove 42 in control piece 40.Shorter section is connected to a kind of larger-diameter section towards the side driving flange to turn to of enough and cylinder barrel, and intermediate pin 35 slips in described section.Have one not draw, tensioned mentioned above between classification between the side of intermediate pin and two sections of through hole.
Intermediate pin 35 has the open ended cavity 66 towards being arranged in cylinder barrel, has stretched out the hole 67 of classification from described cavity, and described hole outwards imports in the truncated portion of bulb 36 vertically standing on the intermediate pin on the axis of intermediate pin.From ball cap 37 substrate of live axle, stretch out blind hole 68, described blind hole converges on the radial hole 69 transverse to live axle, and described radial hole outwards imports between tapered roller bearing 13 and tapered roller bearing 15.Region between tapered roller bearing 15 and Simmer ring 75 is connected with the inner chamber of shell 10 in not concrete mode of showing in fluid, has and drive flange 17 and cylinder barrel 30 in described inner chamber.
Current, when cylinder room remittance portion 32 at work leave high voltage control opening rear open to the portion that mills out 63 in the control side 47 of control piece 40 time, the oily passing hole 64 and 65 that reduces pressure flows in fluid chamber, described fluid chamber by the free volume of groove 42 and the through hole 38 of cylinder barrel 30 the free volume comprising the volume of the cavity 66 in intermediate pin and form.In this case, work as flow controller and form first throttle device in hole 64 and 65.Namely fluid chamber works as a kind of volume as fluid container, even if but described volume is closed low pressure is not but caused the pressure jump before flow controller due to the compressibility of oil, namely mill out pressure jump in portion 63 here, because a certain amount of oil must be had to flow into for the pressure change of fluid container.
Current, first fluid path directs into shell inner chamber from fluid chamber by the gap between the groove 42 of control piece 40 and the end section 43 of adjusting pin 44 or directs into from the suction ports of pump in the passage that the low voltage control opening 59 control piece is guided.In this case, work as flow controller in described gap.Second fluid path by the hole 67 in intermediate pin 35, hole 68 and 69 in live axle 16 and on the one hand tapered roller bearing 13 and 14 and on the other hand tapered roller bearing 15 direct in shell inner chamber.In this case, first hole 67 and the yardstick from the truncated portion of the central authorities intermediate pin 35 to the through flow cross section in the hole 68 in live axle work as flow controller.Namely be two flow controllers in fluid container downstream, be namely on the one hand gap between the groove 42 of control piece 40 and the end section 43 of adjusting pin 44 and be that hole 67 and the through flow cross section on the other hand from the truncated portion of the central authorities intermediate pin 35 to the hole 68 in live axle are in parallel mutually and jointly form the second throttling arrangement on the other hand.In this case, the effective through flow cross section of this second throttling arrangement is relevant with the loxosis of cylinder barrel, because relevant with the loxosis of cylinder barrel 30 to the size of the through flow cross section in the hole 68 in live axle from the truncated portion of the central authorities intermediate pin 35.When pump is at zero stroke or when working close to zero stroke and when the loxosis of cylinder barrel 30 is minimum, as visible by means of Fig. 2, the truncated portion on the bulb 36 of intermediate pin 35 is opposed to the hole 68 in live axle 16.Hole 37 in intermediate pin and the through flow cross section between the hole 68 in live axle are maximum.Thus, the effective open cross-section of the second throttling arrangement is maximum and restriction effect is small.This is contrary with the following fact, namely in zero stroke, the minimum volume of dead volume, i.e. active chamber be maximum and pressure therefore in active chamber reduces a kind of value determined, a large amount of decompression oil must to be flow in fluid container by first throttle device and must flow in the area of low pressure of pump from there through the second throttling arrangement from active chamber.Otherwise, when pump carries out carrying in total travel and cylinder barrel 30 has maximum loxosis, as visible by means of Fig. 1, the truncated portion on the bulb 36 of intermediate pin 35 maximally deflects and the hole 67 in intermediate pin and the through flow cross section between the hole 68 in live axle are minimum.Because dead volume is minimum in total travel, so the decompression oil of the pettiness that only flows.Via the minimum through flow cross section of the second throttling arrangement, even if utilize the oil of the pettiness in fluid container to flow into also set up certain pressure, thus obtain the low cascade of Pressure Drop.
In addition as according to shown in the embodiment of Fig. 1 to 3, the triggering energy with the flow controller of the through flow cross section that can change by other mechanism such as coupling transmission device or spring hydraulic or electrically such as realized by electromagnet or servomotor.
Control piece need not be independently part, but can also consist of connecting plate in other embodiments.Here first it is envisaged that, the hydrostatic axial piston machine in inclined disc type mode of structure, there is stroke volume that is constant or that can adjust, or in clino-axis type mode of structure, there is the hydrostatic axial piston machine of constant stroke volume.Concerning described piston machine, the low cascade of Pressure Drop with first throttle device, fluid container and the second throttling arrangement is also possible.
Same energy it is envisaged that, in following meaning, cancel the second throttling arrangement, the groove 42 namely in control piece to area of low pressure all open wide and therefore groove and may exist, to its open wide cylinder body 30 in through hole in there is low pressure all the time at work.Control piece by the iron material manufacture of high value, when not occurring to be raised by the main pressure of the inflow of the oil that reduces pressure in groove 42, the beam of oil so described iron material also can stand to reduce pressure.
Show the cylinder barrel 30 of hydrostatic piston machine, control piece 40 and connecting plate 12 with launching in Fig. 4 is to 7.Wherein it such as refers to the axial piston machine of inclined disc type mode of structure, with the axial piston machine of clino-axis type mode of structure or radial piston machine.Cylinder barrel has nine cylinder rooms, and in described cylinder room, nine pistons 18 can implement stroke motion.Visible from accompanying drawing, which kind of position piston occupies in the moment determined.A part for piston is just in time arranged in crush stroke, and in this crush stroke, pressure medium is expressed to by the high voltage control opening 58 in control piece 40 in the high-pressure channel 76 in connecting plate 12 from active chamber 31.Another part of piston is arranged in intake stroke, and in this intake stroke, pressure medium is flowed in active chamber by the low voltage control opening in control piece 40 from the low-pressure channel 77 of connecting plate.A piston is in Zone switched 60, and in this is Zone switched, described piston is from low pressure to high pressure conversion, and another piston is in Zone switched 61, and in this is Zone switched, another piston described is changed from high pressure to low pressure.In Zone switched, there is pre-control opening, pressure is reduced fluid path and is guided to area of low pressure or to storage tank by first throttle device 80, fluid container 81 and the second throttling arrangement from described pre-control opening.
According in the embodiment described in Fig. 4, in the structure of throttling arrangement, this embodiment is corresponding to the embodiment in Fig. 1 to 3, and the second throttling arrangement is consisted of two flow controllers 82 and 83 arranged that walk abreast mutually.The through flow cross section of flow controller 83 to change.First throttle device is consisted of single flow controller 80.In Fig. 1 is to 3, flow controller 80 is formed basically by inclined hole 64, flow controller 82 is consisted of the gap between the end section 43 of adjusting pin 44 and control piece 40, and covering between flow controller 83 passing hole 67,68 and 69 that can adjust and the hole 67 and 68 changed along with the oblique angle of cylinder barrel 30 and forming.Because the through flow cross section of the first throttle device consisted of flow controller 80 is less than the through flow cross section of any one in two flow controllers 82 and 83 of the second throttling arrangement, so in the diagram, flow controller 80 is less than flow controller 82 and 83 ground and draws.At work when remittance portion, cylinder room 32 have left high voltage control opening, it is just opened to the hole with flow controller 80.After certain rotational angle, remittance portion, cylinder room not only cover apertures also hides low voltage control opening 59, thus for the corner area determined, the fluid existed between hole and low voltage control opening connects.
Flow controller 80,82 and 83 in the diagram mutually between and layout in fluid container not only for the hydrostatic axial piston machine of clino-axis type mode of structure, and the hydrostatic piston machine for other is such as all to imagine with the axial piston machine of inclined disc type mode of structure or radial piston machine.This is also suitable for according to the layout of Fig. 5 to 7.
When the embodiment of institute's schematic presentation in Figure 5, the second throttling arrangement is consisted of single unalterable flow controller 82 in its through flow cross section.
When the embodiment of institute's schematic presentation in figure 6, deposit again two flow controllers 80 and 82 in Figure 5.Different from according to the embodiment described in Figure 4 and 5, the current moveable piston 85 by restricted volume carrys out Tectono-fluids container 81.On side, piston is connected with described volume, and acts on spring in another piston side.Pressure can be kept constant on the longer time period by means of described structure or almost constant.Spring also can be similar to magnet or air kind and replace like that in hydropneumatic storage.
When the embodiment of institute's schematic presentation in the figure 7, form the second throttling arrangement by single unalterable flow controller 82 in its through flow cross section.First throttle device is consisted of two flow controllers 80, these two flow controllers have constant through flow cross section and passing hole is formed, described hole is opened wide disconnected from each otherly in Zone switched 61 of control piece 40, and the hole of one of them hole compared to other on low voltage control opening 59 is closer opened wide.Therefore at work, when active chamber is changed from the high voltage control opening 58 of control piece 40 to low voltage control opening 59, first just from low voltage control opening 59 away from hole, be then these two holes, finally just on low voltage control opening 59, the comparatively near hole existed is opened wide towards remittance portion, corresponding cylinder room 32.Wherein when these two holes are also when opening to remittance portion, cylinder room, remittance portion, cylinder room 32 has reached low voltage control opening 59 corresponding to according to the embodiment of Fig. 4 to 6, thus first from a hole, is then only also produced the fluid that relatively low pressure controls opening 59 connect from these two holes by remittance portion, cylinder room 32.
In fig. 8 detail display can adjust in its stroke volume with the axial piston machine of hydrostatic inclined disc type mode of structure first for there is the pump of hydraulic oil or motor operation and there is the shell 100 that the shell main part 101 comprising can-like is called for short the connecting plate 102 of shell tank and cover shell tank, described connecting plate constructs high pressure connecting end and low pressure, suction or storage tank connecting end.Live axle 105 can be supported rotationally by tapered roller bearing 103 and 104 in the bottom of shell tank 101 and in connecting plate 102, cylinder barrel 106 is rotatably coupled with described live axle is antitorque, described cylinder barrel is under the effect of central spring 107 and rest under the effect of the pressure extraly at work on control panel 108, and described control panel is rotatably arranged about connecting plate is antitorque between cylinder barrel 106 and connecting plate 102.Smooth at cylinder barrel, surface of contact between control panel and connecting plate.
Cylinder barrel has equally distributed cylinder room 29 in the circumferential, and described cylinder room is opened wide to swash plate 109, and described swash plate can swingingly be placed in shell tank 101.In cylinder room 29, piston 118 is longitudinally movably guided, and described piston has the piston rod 119 and spherical piston head 120 that are constructed to cylinder, and described piston head is hingedly connected with piston shoes 121, and described piston shoes are used for piston to be supported on swash plate 109.Piston 118 utilizes piston rod 119 to limit active chamber 31 in cylinder room 29, and the volume of described active chamber changes along with the stroke of piston.The side deviating from swash plate 109 of cylinder barrel 30 exists remittance portion, cylinder room 32, wherein has respectively and import passage guide cylinder room.Remittance portion, cylinder room is positioned on the pitch circle identical with cylinder room, thus remittance passage is parallel to the axis trend of cylinder barrel, and is corresponding to the bending gap of pitch circle.Import the part that passage is active chamber in theory, because pressure medium is compressed when piston runs repeatedly and reduces pressure inside it, but conveying can not be used for, but form the part of the dead volume of active chamber.
In intake stroke, piston 118 utilizes piston shoes 121 to remain under the effect of central spring 107 on swash plate 109, and wherein said central spring is acted on piston by annular disk, the pin extended between live axle and cylinder barrel do not specifically not illustrated, time stagnant ball 110 and time stagnant plate 111 and piston shoes 121.
In control panel 102, there is the high voltage control opening of the kidney shape and the low voltage control opening of the kidney shape, in described low voltage control opening current have at work height can reach the storage tank pressure of 5 bar or low on-load pressure.For clarity sake depict two one-i.e. high voltage control openings 58 controlled in opening in fig. 8, even if it itself is sightless in the cross section for being arranged in plotting planes.Control to have between opening as in the other embodiments so-called Zone switched at two, in Zone switched, high pressure connecting end from low pressure connecting end to pump of the connection of active chamber and oppositely converting.Zone switched 61 can be identified in fig. 8.When active chamber is changed between the control opening of control panel 108, the pressure medium compression in active chamber or decompression.This should impact type not occur, because pump otherwise can be very noisy and can loaded members tempestuously.
For from low pressure to the switching of high pressure therefore, it is possible to arrange switching slot as according to Fig. 1 to the embodiment of 3.
For the switching between high pressure and low pressure, in Zone switched 61, in the spacing in low voltage control opening front, stretch out hole 125, described hole is further guiding and working as flow controller 80 by the through ground of control panel 108 and in connecting plate 102.Described hole imports in fluid chamber 81, and described fluid chamber constructs in connecting plate 102.Second hole 126 of working as flow controller 82 from fluid chamber 81 by the material of connecting plate 102 through guide and import the inside of shell 100.
Current, when the backward hole 80 that high voltage control opening is left in cylinder room remittance portion 32 is at work opened, reduce pressure in oily passing hole 80 incoming fluid chamber 81.Namely fluid chamber works as a kind of volume as fluid container, even if but described volume is closed low pressure is not but caused the pressure jump in the pressure jump before flow controller i.e. remittance place of Zone switched 61 mesopores 125 here due to the compressibility of oil, because must flow into a certain amount of oil for the pressure change of fluid container.
Raised by the pressure of fluid container and appearance during switching in described fluid container, also first the stress level in active chamber is remained on during switching in the level relative to atmospheric pressure raising, thus phenomenon such as cave and poor suction properties that therefore the formation of bubble also occur are reduced or improve.
reference character list
10 shells
11 shell main parts
12 connecting plates
13 tapered roller bearings
14 tapered roller bearings
15 tapered roller bearings
16 live axles
17 drive flange
18 pistons
19 piston rods
20 piston heads
Spherical caps on 2117
22 times stagnant plates
The rotation axis of 2316
29 cylinder rooms
30 cylinder barrels
31 active chambers
32 remittance portion, cylinder rooms
The rotation axis of 3330
35 intermediate pins
The bulb of 3635
Ball cap in 3716
38 through holes
40 control pieces
41 guide rails
Groove in 4240
The end section of 4344
44 adjusting pins
45 regulating levers
The support side of 4640
The control side of 4740
The supporting surface of 4830
58 high voltage control openings
59 low voltage control openings
Zone switched on 6040
Zone switched on 6140
62 switching slot
63 mill out portion
64 inclined holes
65 holes
Cavity in 6635
Hole in 6735
Elongated hole in 6816
Radial hole in 6916
75 Simmer rings
76 high-pressure channels
77 low-pressure channels
80 flow controllers
81 fluid containers
82 flow controllers
83 flow controllers
85 pistons
86 springs
100 shells
101 shell tanks
102 connecting plates
103 tapered roller bearings
104 tapered roller bearings
105 live axles
106 cylinder barrels
107 central springs
108 control panels
109 swash plates
110 times stagnant balls
111 times stagnant plates
118 pistons
119 piston rods
120 piston heads
121 piston shoes
125 holes
126 holes.
Claims (13)
1. hydrostatic piston machine, especially hydrostatic axial piston machine, has low-pressure channel (77) and has high-pressure channel (76), has the shell (10 holding oil return, 100), there is the cylinder body (30 of rotation, 106), described cylinder body is at control piece (40, 108) go up setting and there is multiple cylinder room (29), in described cylinder room, being provided with the piston (18 implementing stroke motion at work, 118) and wherein each piston can by remittance portion, cylinder room (32) in an alternating fashion by described control piece (40, 108) low voltage control opening (59) is connected with low-pressure channel (77) and passes through described control piece (40, 108) high voltage control opening (76) is connected with high-pressure channel (76), wherein at described control piece (48, 108) have two Zone switched (60,61) between described low voltage control opening (59) and described high voltage control opening (58) on, wherein piston (18, 118) in dead point, its moving direction is reversed, and the inswept described control piece in corresponding remittance portion, cylinder room (32) (40, 108) Zone switched (60,61), and wherein in Zone switched (61), there is pre-control opening (63, 125), described Zone switched remittance portion, middle cylinder room (32) from described high voltage control opening (58) towards described control piece (40, 108) low voltage control opening (59) conversion, remittance portion, described cylinder room (32) reduced fluid path by described pre-control opening via the pressure with first throttle device (80) and is connected with described area of low pressure before it is opened to described low voltage control opening (59), it is characterized in that, described pressure reducing fluid path configuration is decompression cascade, described decompression cascade also has at least one and is in the second throttling arrangement (82 in connecting with first throttle device except described first throttle device (80), 83) and at two be in each other between the throttling arrangement in series connection and there is fluid container (81).
2. according to hydrostatic piston machine according to claim 1, have the stroke volume that can adjust, it is characterized in that, the effective passage section of throttling arrangement (82,83) can change along with stroke volume.
3. according to the hydrostatic piston machine described in claim 1 or 2, it is characterized in that, in described pressure reducing fluid route guidance to the low voltage control opening (59) of described control piece (40) or direct in described low-pressure channel (77).
4. according to the hydrostatic piston machine described in claim 1 or 2, it is characterized in that, described pressure reducing fluid route guidance is to described shell (10; 100) in the region of accommodation oil return.
5. according to the hydrostatic piston machine according to any one of claim 1 to 4, it is characterized in that, described first throttle device (80) is at least in part at control piece (40; 108) structure in.
6. according to hydrostatic piston machine according to claim 5, it is characterized in that, described first throttle device (80) is by the hole (64,65 in described control piece (40); 125) construct.
7. according to hydrostatic piston machine in any one of the preceding claims wherein, it is characterized in that, it is configured with at the upper driving flange (17) constructed of live axle (16) as axial piston machine with clino-axis type mode of structure, described driving flange hingedly supports the piston (18) be contained in cylinder body (30), described control piece (40) there is the groove (42) of central authorities and described groove (42) at least as the part of fluid container (81) at described first throttle device (80) downstream part in pressure reducing fluid path.
8. according to hydrostatic piston machine according to claim 7, it is characterized in that, it is configured to the clino-axis type machine that can adjust in its stroke volume and in the drop-center (42) of described control piece (40), embedded in the adjusting pin (44) of the regulating mechanism for adjusting stroke volume.
9. according to hydrostatic piston machine according to claim 8, it is characterized in that in described drop-center (42), between described control piece (40) and described adjusting pin (44), there is gap and this gap belongs to the second throttling arrangement as flow controller (82).
10. according to claim 7, hydrostatic piston machine described in 8 or 9, it is characterized in that, described cylinder body (30) has the through hole (38) of central authorities, the intermediate pin (35) of the described cylinder body of guiding (30) is contained in described through hole, described intermediate pin is hingedly supported on the driving flange (17) of described live axle (16), and the groove (42) in the through hole (38) of the central authorities in described cylinder body (30) and described control piece (40) is opened each other, and the free volume of described through hole (38) and described groove (42) and be in described first throttle device (80) and described second throttling arrangement (82 as fluid container (81) in pressure reducing fluid path, 83) between.
11. according to hydrostatic piston machine according to claim 10, it is characterized in that, the section (67) in described pressure reducing fluid path by described intermediate pin (35) guiding and section (68,69) by described live axle (16) guiding, and in transition between these two sections from stroke volume about set different throttling cross sections.
12. according to hydrostatic piston machine according to claim 11, it is characterized in that, described pressure reducing fluid path to be directed in the leakage region of described shell (10) by least one rolling bearing for described live axle (16) (13,14,15) by the part of described intermediate pin (35) and described live axle (16) and described rolling bearing (13,14,15) is tapered roller bearing.
13., according to the hydrostatic piston machine according to any one of claim 1 to 6, is characterized in that, it is axial piston machine in clino-axis type mode of structure and described fluid container (81) is configured in shells (102).
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102014208406.7A DE102014208406A1 (en) | 2014-05-06 | 2014-05-06 | Hydrostatic piston machine |
| DE102014208406.7 | 2014-05-06 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN105089961A true CN105089961A (en) | 2015-11-25 |
| CN105089961B CN105089961B (en) | 2018-12-18 |
Family
ID=54336447
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510222194.4A Active CN105089961B (en) | 2014-05-06 | 2015-05-05 | Hydrostatic piston machine |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN105089961B (en) |
| DE (1) | DE102014208406A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109154284A (en) * | 2016-05-19 | 2019-01-04 | 伊纳斯有限公司 | A kind of hydraulic device |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102018215362A1 (en) * | 2018-09-11 | 2020-03-12 | Robert Bosch Gmbh | Axial piston machine |
| DE102019205140A1 (en) * | 2019-04-10 | 2020-10-15 | Robert Bosch Gmbh | Axial piston machine with valve spools integrated in the connection plate |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101326365A (en) * | 2006-04-10 | 2008-12-17 | 布鲁宁赫斯海诺马帝克有限公司 | Hydrostatic piston engine with rotatable control disc |
| DE102011009537A1 (en) * | 2011-01-27 | 2012-08-02 | Robert Bosch Gmbh | Hydrostatic machine, in particular axial piston machine |
| DE102012218888A1 (en) * | 2011-11-12 | 2013-05-16 | Robert Bosch Gmbh | Hydrostatic piston machine |
| US20130167957A1 (en) * | 2012-01-04 | 2013-07-04 | Prashant K. Rajput | Hydraulic piston pump with a variable displacement throttle mechanism |
| CN103511242A (en) * | 2012-06-14 | 2014-01-15 | 罗伯特·博世有限公司 | Hydrostatic piston machine |
| CN103573573A (en) * | 2012-08-04 | 2014-02-12 | 罗伯特·博世有限公司 | Hydrostatic axial piston machine |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5230274A (en) | 1992-02-11 | 1993-07-27 | Vickers Incorporated | Variable displacement hydraulic pump with quiet timing |
| JPH08144941A (en) * | 1994-11-21 | 1996-06-04 | Uchida Yuatsu Kiki Kogyo Kk | Pulsation reduction device for cam plate type axial piston pump |
| DE19706114C9 (en) * | 1997-02-17 | 2014-02-06 | Linde Hydraulics Gmbh & Co. Kg | Device for pulsation reduction on a hydrostatic displacement unit |
| DE19818721A1 (en) * | 1998-04-27 | 1999-10-28 | Mannesmann Rexroth Ag | Hydrostatic machine |
| DE10034857A1 (en) * | 2000-07-18 | 2002-01-31 | Liebherr Machines Bulle S A | Hydrostatic axial piston machine |
-
2014
- 2014-05-06 DE DE102014208406.7A patent/DE102014208406A1/en active Pending
-
2015
- 2015-05-05 CN CN201510222194.4A patent/CN105089961B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101326365A (en) * | 2006-04-10 | 2008-12-17 | 布鲁宁赫斯海诺马帝克有限公司 | Hydrostatic piston engine with rotatable control disc |
| DE102011009537A1 (en) * | 2011-01-27 | 2012-08-02 | Robert Bosch Gmbh | Hydrostatic machine, in particular axial piston machine |
| DE102012218888A1 (en) * | 2011-11-12 | 2013-05-16 | Robert Bosch Gmbh | Hydrostatic piston machine |
| US20130167957A1 (en) * | 2012-01-04 | 2013-07-04 | Prashant K. Rajput | Hydraulic piston pump with a variable displacement throttle mechanism |
| CN103511242A (en) * | 2012-06-14 | 2014-01-15 | 罗伯特·博世有限公司 | Hydrostatic piston machine |
| CN103573573A (en) * | 2012-08-04 | 2014-02-12 | 罗伯特·博世有限公司 | Hydrostatic axial piston machine |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109154284A (en) * | 2016-05-19 | 2019-01-04 | 伊纳斯有限公司 | A kind of hydraulic device |
Also Published As
| Publication number | Publication date |
|---|---|
| DE102014208406A1 (en) | 2015-11-12 |
| CN105089961B (en) | 2018-12-18 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN105089961A (en) | Hydrostatic piston machine | |
| US20110041681A1 (en) | Positive-displacement machine | |
| CN1965169A (en) | Linear drive | |
| CN106103145B (en) | Active damper system for vehicle | |
| CN104797821A (en) | Compressor valve system and assembly | |
| JP2016519250A (en) | Swash plate type axial piston pump | |
| SE533152C2 (en) | Curved shaft pump / motor with variable displacement | |
| US20120282114A1 (en) | Air pump | |
| US20090120283A1 (en) | Combination of a chamber and a piston, a pump, a motor, a shock absorber and a transducer incorporating the combination | |
| CN103079769A (en) | Hydraulic impact mechanism for use in equipment for treating rock and concrete | |
| CN1934354B (en) | Long-piston hydraulic machines | |
| CN106593535B (en) | Actively driven fluid mechanism | |
| AU2002308385A1 (en) | A combination of a chamber and a piston, a pump, a motor, a shock absorber and a transducer incorporating the combination | |
| CN102362070A (en) | Reciprocating compressor | |
| CN101113772B (en) | Hydraulic damper for use with vehicle brake assembly piston pump | |
| CN104776072B (en) | Hydraulic axis | |
| US3180274A (en) | Silent variable delivery hydraulic pump | |
| CN102937087B (en) | Plunger pump in double swash plate structure | |
| JP2015504013A (en) | Hammer equipment | |
| US3619087A (en) | Free piston-type pump | |
| CN106593537B (en) | Plunger hydraulic mechanism | |
| KR101418747B1 (en) | Apparatus for fluid supply | |
| US11486372B2 (en) | Rotary barrel pump having separate guiding means and centering means for the barrel | |
| CN109296816B (en) | Mechanical switching dispensing device | |
| US20230358217A1 (en) | Partial stroke fluidic pump-motor with high mechanical efficiency |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |