CN103958893A - Hydrostatic piston machine - Google Patents
Hydrostatic piston machine Download PDFInfo
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- CN103958893A CN103958893A CN201280058300.4A CN201280058300A CN103958893A CN 103958893 A CN103958893 A CN 103958893A CN 201280058300 A CN201280058300 A CN 201280058300A CN 103958893 A CN103958893 A CN 103958893A
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- Prior art keywords
- opening
- mouth
- plunger cavity
- piston engine
- pressure
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B11/00—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation
- F04B11/0008—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using accumulators
- F04B11/0016—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using accumulators with a fluid spring
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/20—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
- F04B1/2042—Valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B2205/00—Fluid parameters
- F04B2205/08—Pressure difference over a throttle
Abstract
A hydrostatic piston machine, in particular an axial piston machine, is disclosed which has a plurality of piston spaces, in which pistons perform a reciprocating movement. Here, a respective piston space can be connected alternately via a control opening in each case to a low-pressure opening and a high-pressure opening. Reversing regions are provided between the low-pressure opening and the high-pressure opening, via which reversing regions a respective piston space is moved in the transition between the low-pressure opening and the high-pressure opening. A mouth is provided in a respective reversing region, via which mouth a respective piston space can be connected to an accumulator element, in particular a pre-compression volume, when the control opening thereof overlaps with one of the mouths during operation of the piston machine.
Description
Technical field
The present invention relates to a kind of according to as described in the preamble hydrostatic plunger machine, the particularly axial piston engine of claim 1.
Background technique
At DE4229544A1, disclose a kind of such piston engine, this piston engine is axial piston engine.This piston engine has the cylinder body being arranged on live axle, and described cylinder body has a plurality of plunger cavities, and each plunger is directed to movingly in described plunger cavity.Corresponding plunger cavity can by processing, the control opening in the end face of cylinder body be alternately connected with high pressure opening with the low-pressure opening of the kidney shape of processing in control panel respectively.The cylinder body that is in operation slides on the end face of control panel.Low-pressure opening and high pressure opening are positioned at common part circle above and are spaced apart from each other in circumferential direction, form thus two transition regions.In region in its upper dead center or top dead center Top Dead Center (TDC) in another in region in its lower dead centre or lower dead center Bottom Dead Center (BDC) in this transition region one of corresponding plunger and in this transition region.One passage with passage mouth leads to (the BDC place of corresponding plunger in this transition region in this transition region) in this transition region, and described passage mouth is connected with precompression volume (PCV).PCV is connected with high pressure opening with throttling arrangement by guiding valve, and PCV can be supplied to high pressure and by throttling arrangement, load lentamente in the situation that guiding valve is opened thus.Seeing in the radial direction, the passage in transition region passes into outside the maximum diameter of low-pressure opening and high pressure opening.The control opening of corresponding plunger cavity has cutout portion, and this cutout portion is positioned at outside the maximum diameter of low-pressure opening and high pressure opening equally, and therefore controlling opening can intersect with described passage.
When cylinder body relatively moves with respect to control panel, the inswept transition region with passage mouth of control opening of corresponding plunger cavity, therefore by the active chamber of plunger cavity and plunger limited boundary by this passage and storage device during definite time of contact, is connected and active chamber in pressure approach rapidly the pressure of PCV, and PCV lentamente by throttling and valve control, towards the connection loading high pressure of high pressure opening.Therefore active chamber was loaded the hydraulic medium under definite pressure before being connected with high pressure opening, and this causes the reduction of the hydraulic medium fluctuation of piston engine.The reason of hydraulic medium fluctuation is, at the plunger cavity of piston engine, when low-pressure opening is transferred to high pressure opening, must overcome pressure difference.This damage except also causing vibration, noise generation hydraulic medium fluctuation and causing due to cavitation.
The shortcoming that described solution has is that, in order to increase pressure by the hydraulic medium supply active chamber of high pressure opening, this causes additional energy charge.Therefore this piston engine has relatively low efficiency.In addition owing to carrying out throttling arrangement and the valve of hydraulic medium connection between high pressure opening and PCV, this piston engine on device technique, construct get up to spend high.
Publication DE102008061349A1 illustrates another mode of execution with the piston engine of the form of axial piston engine.At this, same setting has the low-pressure opening of the kidney shape and the control panel of high pressure opening.The passage with passage mouth leads to respectively in the corresponding transition region between low-pressure opening and high pressure opening.The passage leading in transition region can be connected with high pressure opening or PCV by control valve, in this transition region in the region of the corresponding plunger of the cylinder body of axial piston engine in its BDC.The passage that leads to other transition region is connected with low-pressure opening or PCV by control valve.Be different from aforesaid solution ground, attainable by this layout, PCV is not only supplied to or on-load pressure by high pressure opening, and is supplied with or loaded by the pressure of the active chamber by corresponding plunger limited boundary.For this reason, the corresponding active chamber of cylinder body was connected with PCV with control valve by the passage leading in transition region in the inswept transition region of control opening of this active chamber (in this transition region in the region of the TDC of corresponding plunger in this transition region) time, and connection between PCV and other transition region is interrupted by described other control valve.Therefore by these passages, having realized mild pressure increases and pressure decreased, has improved thus the noise situations of piston engine.
The shortcoming of this solution be to have a plurality of hydraulic medium pipelines and two for control PCV valve piston engine on device technique, spend high structure.
Summary of the invention
On the other hand, the object of the invention is to propose a kind of piston engine (or piston machine) of eliminating described shortcoming.
This object realizes by the hydrostatic plunger machine according to the feature of claim 1.
Other favourable further schemes of the present invention are themes of other dependent claims.
According to the present invention, hydrostatic plunger machine, particularly axial piston engine have a plurality of plunger cavities, arrange respectively one and can implement reciprocating plunger in described plunger cavity.Corresponding plunger cavity is alternately connected with high pressure opening with the low-pressure opening of controlling component by controlling opening, and described controlling component can be control panel.Low-pressure opening and high pressure opening are separated from one another by two transition regions, and described transition region is particularly roughly arranged in the region of the corresponding dead center position of plunger.In corresponding transition region, a mouth is set respectively, this mouth is connected with memory cell (pressure compensation volume Pressure Recuperation Volume (PRV)).At this, arrange like this control opening of mouth, low-pressure opening and high pressure opening and plunger cavity, PRV is loaded by the plunger cavity that moves to low-pressure opening from high pressure opening when with piston engine, and PRV load the plunger cavity that moves to high pressure opening from low-pressure opening.
The advantage that this solution has is: be different from prior art ground, do not need additional valve and a large amount of for the plunger cavity of PRV and transition region being carried out to pressure controlled hydraulic medium passage, on device technique, construct extremely simply and inexpensively thus this piston engine.In addition, storage device advantageously loads by the plunger cavity that moves to low-pressure opening from high pressure opening via transition region.Then,, before the pressure of plunger cavity reduces via low-pressure opening, the pressure energy of this plunger cavity loads PRV.Therefore do not need the additional-energy for loading to PRV, piston engine has relatively high efficiency thus.
Advantageously, plunger and plunger cavity limit the border of dead center volume jointly, and this dead center volume is less than significantly the storage volume of PRV or reclaims volume.Therefore be provided for fully supplying with by PRV the hydraulic medium of the plunger cavity in transition region.In addition, when the plunger cavity with wait being loaded connects, therefore the pressure drop of PRV is also relative low.
Show especially advantageously, storage volume is at least about 7.5 times of dead center volume.
In another structural scheme of the present invention, controlling opening, low-pressure opening and high pressure opening and mouth is constructed as follows, make when plunger cavity is connected with corresponding mouth, the corresponding opening of controlling is not connected with high pressure opening with low-pressure opening, avoids thus the connection that causes energy loss between low-pressure opening or high pressure opening and PRV.Therefore PRV is only connected with plunger cavity formation hydraulic medium.
At this, described mouth can have different relative to each other opening transverse incisions.At this, described mouth has length different in the circumferential direction with respect to spin axis and/or at different in the radial direction width.Therefore by the length in circumferential direction of particularly slot-shaped mouth, substantially determine corresponding mouth and control accordingly the time of contact between opening, and mouth and the crossing width in the radial direction controlled accordingly between opening have been determined the hydraulic medium volume flowrate between memory cell and plunger cavity accordingly.
At this, described mouth and/or control opening are preferably constructed as follows, make between memory cell and plunger cavity, to exchange a volume due to PRV and plunger cavity and the hydraulic medium volume flowrate of maximum possible when crossing, therefore can realize maximum energy and reclaim.
In addition particularly so design mouth and/or control opening, making after control opening is no longer connected with low-pressure opening or high pressure opening, corresponding mouth is connected with plunger cavity as early as possible.
In another structural scheme of the present invention, when the pressure in memory cell is almost equal with pressure in the plunger cavity being connected with mouth, separates described mouth and control the connection between opening.
From the spin axis of piston engine in the radial direction, described mouth is preferably configured in controlling component outside the maximum outside diameter of low-pressure opening and/or high pressure opening, and wherein, low-pressure opening and/or high pressure opening have substantially invariable external diameter.In addition the control opening of plunger cavity has the cutout portion being positioned at equally outside described external diameter.Therefore, aspect the time of contact at mouth and when controlling opening and intersecting, design extremely neatly mouth and control the geometrical shape of opening and the size of the hydraulic medium volume flowrate between PRV and corresponding plunger cavity.Controlling observing in the circumferential direction of spin axis of opening, cutout portion can be configured in to be controlled about middle of opening and particularly has u shape.In addition advantageously, described cutout portion ratio in the circumferential direction of controlling opening is controlled opening much shorter.
In order to increase the intersecting area of controlling between opening and mouth, described mouth is configured to slot-shaped and roughly in circumferential direction, extends with respect to spin axis at this.
Additionally or alternatively, mouth can be configured in the bearing housing of sliding bearing of the cylinder body with plunger cavity.Corresponding plunger cavity also has other control openings or the conversion opening that can alternately be connected with mouth except controlling opening.The advantage that this solution has is, described other control openings or conversion opening owing to being configured in other members rather than in control panel, can substantially have nothing to do in low-pressure opening and the crossing control opening of high pressure opening construct.
Preferably, changing accordingly opening is being arranged in cylinder body in the radial direction.
Accompanying drawing explanation
Describe with reference to the accompanying drawings preferred embodiment of the present invention below in detail.
In accompanying drawing:
Fig. 1 with plan view illustrate according to the first embodiment according to the control panel of piston engine of the present invention,
Fig. 2 illustrates according to the cylinder body of the first embodiment's piston engine with worm's eye view,
Fig. 3 illustrates the schematically illustrated Local map according to the control panel of the first embodiment's piston engine,
Figure 4 and 5 illustrate respectively the sketch having according to the different parameters of the first embodiment's piston engine, and
Fig. 6 illustrates according to the second embodiment's piston engine with schematic sketch.
Embodiment
In Fig. 1 in order to illustrate that hydrostatic plunger machine according to the present invention shows the controlling component with the form of control panel 1 with plan view.Described piston engine is axial piston pump.The basic structure of axial piston pump is fully open by prior art, therefore can omit explanation completely below.
Control panel 1 has the high pressure opening 4 of low-pressure opening 2 and the kidney shape of the kidney shape, and this high pressure opening is divided into three essentially identical sections by two for mechanically proposing high-intensity contact pin 6.Low pressure-and high pressure opening 2 and 4 along common round section extend.Control panel 1 is configured to ring-type and at center, has circular space 8, and the live axle of axial piston pump can pass this space.Low-pressure opening 2 is connected with low-voltage interface and high pressure opening 4 is connected with the high voltage interface of axial piston pump.
The cylinder body 10 of axial piston pump is shown with worm's eye view in Fig. 2.When axial plunger pump operation, this cylinder body utilizes on the slip surface 14 of its distolateral 12 control panel 1 at Fig. 1 and slides.A plurality of control openings 16 lead in described distolateral 12, these control openings be configured to respectively the kidney shape and along a common round section extend.At this, control accordingly opening 16 with unshowned, with respect to the spin axis parallel interval of cylinder body 10 plunger cavity arranging of turning up the soil, be connected, plunger is directed to movably and defines the border of active chamber in described plunger cavity.
In service at piston engine, control in the anticlockwise sense of rotation of opening 16 in Fig. 1 and be alternately connected with high pressure opening 4 with low-pressure opening 2.At this, realize like this to-and-fro motion that is arranged in the plunger in cylinder body 10, make this plunger in the region of high pressure opening 4, carry out compression stroke and in the region of low-pressure opening 2, carry out intake stroke.
In Fig. 1, in anticlockwise sense of rotation, the first transition region 18 is being set between low-pressure opening 2 and high pressure opening 4 and the second transition region 20 is being set between high pressure opening 4 and low-pressure opening 2.At this, these transition regions are positioned at the region, dead point of plunger motion.In the first transition region 18, in the region of plunger in its bottom dead-centre; And in the second transition region 20, in the region of plunger in its inner dead centre.Therefore described the first transition region 18 is such transition regions, carries out the transfer from low-pressure opening 2 to high pressure opening 4 of control opening 16 in Fig. 2 in this transition region when by axial piston pump delivery hydraulic pressure medium; And said the second transition region 20 is such transition regions, in this transition region, control the transfer of opening 16 from high pressure opening 4 to low-pressure opening 2.
Plunger cavity is controlled opening 16 at it and is filled hydraulic medium with low-pressure opening 2 period of contact, and wherein, the stress level in plunger cavity is roughly consistent with the stress level of low-pressure opening 2.When contacting with high pressure opening 4, hydraulic medium is squeezed from plunger cavity 16, and here the stress level in plunger cavity is approximately corresponding to the stress level of high pressure opening 4.In order to avoid compression shock when plunger cavity comes in contact with low pressure or high pressure opening 2 or 4 after transition region 18 and 20, in corresponding transition region 18 or 20, a mouth 22 or 24 is set in control panel 1.At this, corresponding transition region 18 or 22 is by corresponding mouth 22 or 24 and be directly connected with memory cell 30 by hydraulic medium pipeline 26 or 28.At this, memory cell 30 as space processing in the cover plate of axial piston pump, wherein this space can be simply together with cover plate with pouring procedure manufacture.Mouth 22 and 24 is schematically illustrated and illustrate enlargedly in Fig. 3 in Fig. 1.
In Fig. 3, can find out, mouth 22 and 24 be configured to slot-shaped and along a common round section extend.In Fig. 3 for the several circumferential shape that schematically show the control opening 16 in Fig. 2 except end segments of high pressure opening 4 and two end segments of low-pressure opening 2 are described better.Described mouth 22 and 24 described low pressure-and high pressure opening 2 and 4 maximum outside diameter outside be configured in the control panel 1 in Fig. 1.
By Fig. 3, found out, control opening 16 and have in the radial direction and low pressure-and high pressure opening 2,4 essentially identical width and along extending with the circle of low pressure-identical with high pressure opening 2,4.For control opening 16 and mouth 22,24 in Fig. 3 are intersected when cylinder body 10 rotates, control the opening transverse incision 32 (also seeing Fig. 2) that opening 16 additionally has u shape.Described opening transverse incision corresponding control opening 16 in circumferential direction general arrangement middle and radially stretch out.At this, the primary section of the Length Ratio control opening 16 in circumferential direction of this opening transverse incision is much smaller.
When the cylinder 10 of Fig. 2 rotates, the opening transverse incision 32 (seeing Fig. 3) of controlling opening 16 intersects with mouth 22 or 24, connects thus between the memory cell in plunger cavity and Fig. 1 30.At this so slot-shaped mouth 22 of design and 24 and the length of opening transverse incision 32, make in mouth 22 and 24 and opening transverse incision 32 while intersecting, control opening 16 and be arranged in the transition region 18 or 20 of Fig. 1 completely and therefore do not exist towards low pressure-or the connection of high pressure opening 2 or 4.This illustrates by schematically illustrated control opening 16 in Fig. 3.In this accompanying drawing, the control opening 16 on the right illustrates with a position at this, described in this position, control opening cylinder body 10 inhours after (this shows by arrow 34) be directly arranged in low-pressure opening 2 while rotating, and opening transverse incision 32 is before this is located immediately at the mouth 22 on the right.When this is controlled opening 16 and continues counter-clockwise rotation, opening transverse incision 32 will intersect with mouth 22.Before control opening 16 contacts with high pressure opening 4, this intersects end.This is equally applicable to the control opening 16 shown in the left side in Fig. 3, described control opening directly after high pressure opening 4 with its opening transverse incision 32 before mouth 24.Therefore,, when further counter-clockwise rotation, it is just crossing with dead slot 24 high pressure opening 4 after that this controls opening 16.Before this control opening 16 contacts with low-pressure opening 2, this intersects end.Therefore memory cell 30 is connected with plunger cavity according to revolving valve principle.
Below according to the working principle of the axial piston pump in machine parameter explanatory drawing 1 to 3, described machine parameter schematically with the form of chart shown in Figure 4 and 5.A plurality of curves about time s in described chart, have been described.In Fig. 4, exemplarily according to different parameters, the process of heightening is shown, at this, heightens in process the low-pressure opening 2 of corresponding plunger cavity from Fig. 1 and arrive high pressure openings 4 through transition regions 18, this plunger cavity in this transition region by precompression.Fig. 5 exemplarily illustrates according to different parameters the process of turning down, at this, turn down the high pressure opening 4 of corresponding plunger cavity from Fig. 1 in process and arrive low-pressure opening 2 through transition region 20, in this transition region, the pressure decreased in plunger cavity and be used to load described memory cell 30.
The opening transverse incision 32 of lower curve 36 in Fig. 4 in this schematically illustrated Fig. 3 and the time of contact between mouth 22, the high value of curve 36 means intersecting of carrying out in time of contact between 0.08 and 0.08102 roughly.
The curve 38 that is arranged in about middle in Fig. 4 illustrates the supply flow of hydraulic medium qualitatively, and the hydraulic medium pipeline 26 in described hydraulic medium opening transverse incision 32, mouth 22 and Fig. 1 on the right of plunger cavity process is arranged among Fig. 3 arrives memory cells 30.This can be seen that, hydraulic medium only exchanges in the time of contact between 0.08 to 0.08102, and wherein said supply flow sharply raises and then slowly declines when the crossing beginning of controlling between opening 16 and mouth 22.Controlling the contact between opening 16 and mouth 22 or intersecting end not long ago, supply flow is also zero substantially.
Curve 40 and curve 42 illustrate pressure to be changed.The numerical value providing on y axle and the parameter providing " pressure " are only only applicable to this two curves.
Curve 40 illustrates the variation on time of contact of pressure in plunger cavity.In the time of 0.08 second, when crossing beginnings of controlling between opening 16 and mouth 22, the pressure in plunger cavity is approximately zero and follow until be elevated to about 110bar while being 0.08102 second time of contact.After described time of contact, pressure also continues to raise, because control opening 16, intersects with the high pressure opening 4 in Fig. 3.Then pressure is elevated to about 300bar in plunger cavity, and this is corresponding to the pressure in high pressure opening 4.
Curve 42 in the chart of Fig. 4 illustrates the pressure in the memory cell 30 in Fig. 1.At this, the mouth in control opening 16 and Fig. 3 22 is approximately 130bar before intersecting to pressure in memory cell 30.Controlling after opening 16 contacts with mouth 22, the pressure in memory cell 30 declines slightly, and pressure (seeing curve 40) in while plunger cavity sharply rises.Therefore, the pressure of the pressure of described plunger cavity and described memory cell 30 between described contact in mutual balance.When finish time of contact, described pressure is in a basic balance at about 110bar at this.The pressure that pressure drop in the memory cell 30 of Fig. 1 is significantly less than in plunger cavity at this raises.Its reason is, the volume of memory cell is obviously greater than the active chamber by plunger cavity and plunger limited boundary.Show advantageously, the volume of memory cell 30 is at least about 7.5 times of dead center volume in corresponding plunger cavity.Therefore the memory cell 30 being connected with plunger cavity to be loaded is not by complete discharge.
At this, the control opening 16 of cylinder body 10 is constructed like this and arranges, makes at every turn an only control opening 16 contact with transition region 18 or 20.This is illustrated by means of the curve 44 in Fig. 4, and this curve illustrates as straight line.This represents by the supply flow of the mouth 24 on the left side in Fig. 3.Because can not control the mouth 24 on the left side in opening 16 and Fig. 3 when the control opening on the right and mouth 22 intersect in Fig. 3, do not intersect, so supply flow is zero during this time of contact.
According to the chart in Fig. 5, explain the process of turning down, the control opening 16 of turning down plunger cavity in process at this moves to low-pressure opening 2 from high pressure opening 4 while rotating in Fig. 3 counter-clockwisely.At this, be illustrated in the variation of the curve 36 to 44 of the Fig. 4 in the process of turning down.At this, thereby lower curve 36 illustrates opening, change and the opening transverse incision 32 of control opening 16 and the time of contact between the mouth 24 in Fig. 3 are shown, wherein, in the large time between 0.1002 and 0.1012 second, intersect.The supply flow of heightening is here zero, and this curve 38 in Fig. 5 illustrates.Pressure in plunger cavity (seeing curve 40) was about 300bar and then during time of contact, drops to about 130bar before intersecting with mouth 24.After intersecting, the pressure in plunger cavity continues to decline, because the control opening in Fig. 3 16 intersects with low-pressure opening 2, the pressure drop in plunger cavity is to the pressure of low-pressure opening 2 thus.Pressure in plunger cavity declines within time of contact, and the pressure of (seeing Fig. 1) in memory cell 30 raises, and the curve 42 in Fig. 5 illustrates this point.This pressure is elevated to 130bar from about 110bar here, and thus, the pressure in the pressure in plunger cavity and memory cell 30 is approximately to equate when finish described time of contact.Therefore, memory cell 30 is filled in the hydraulic medium from plunger cavity again during described time of contact, therefore realizes energy and reclaims.Hydraulic medium in plunger cavity therefore for load to memory cell 30 and not markon's land used flow out to low-pressure opening 2.Therefore, the efficiency of piston engine is relatively high because in the energy loss occurring in turning down process, by memory cell 30, stored and the process of heightening in used.
Control opening 16 in Fig. 3 can regulate by its configuration scheme with the time of contact of mouth 22 or 24.At this, the effect length time of contact of mouth 22 and 24 in circumferential direction, wherein in the situation that length is longer, correspondingly increased time of contact.In addition the width of intersecting area or mouth 22 and 24 are selected like this at width in the radial direction and the width of opening transverse incision 32, make pressure and the basic balance mutually of the pressure in memory cell 30 (seeing Fig. 1) in described inner plunger time of contact chamber.Ideally, when between plunger cavity and memory cell 30 during pressure balance, finishing control opening 16 and mouth 22 or 24 intersects respectively.Control between opening 16 and mouth 22 or 24 intersect preferably control opening 16 and low pressure-or high pressure opening 2 or 4 between crossing end after carry out soon.Therefore design like this surface of contact, make can exchange the supply flow of maximum possible between plunger cavity and memory cell 30, this causes maximum energy to reclaim.Therefore, memory cell 30 is connected with plunger cavity according to revolving valve principle.
Fig. 6 illustrates with according to the piston engine of the form of the second embodiment's axial piston pump with schematic view.Be different from aforesaid embodiment ground, mouth 46 and 48 is not to be configured in control panel, but is configured in bearing housing 50, and cylinder body 52 is slidably mounted in this bearing housing.
Cylinder body 52 is connected with live axle 54 regularly, and this live axle is bearing in unshowned casing by swivel bearing 56 and 58 in its end segments.A plurality of plunger cavities are turned up the soil and are arranged in cylinder body 52 with respect to spin axis 60 parallel interval, upper plug shown in Figure 6 chamber 62 and lower plunger chamber 64.A plunger is directed to movingly in described plunger cavity respectively, the plunger 66 of plunger cavity 62 shown in Figure 6 and the plunger 68 of plunger cavity 64.Corresponding plunger 66 is hingedly connected with plunger pin 70 or 72 in a side of cylinder body 52 at it dorsad with 68, and when cylinder body 52 rotation, plunger 66 and 68 passes through described plunger pin and slides on swash plate 74.
Cylinder body 52 utilizes the outer circumferential face 76 of this cylinder body to be bearing in slidably in bearing housing 50.For the sake of simplicity, in Fig. 6, the obvious each interval of the inner peripheral surface of the outer circumferential face of cylinder body 52 76 and bearing housing 50 78 is turned up the soil and illustrated.
Upper mouth 46 in Fig. 6 is connected with a memory cell or PRV82 by hydraulic medium pipeline 80, and lower mandible portion 48 is connected with PRV82 by hydraulic medium pipeline 84.At this, mouth 46 and 48 is arranged in the transition region of piston engine.Upper mouth 46 in Fig. 6 is used herein to the pressure in the plunger cavity increasing between low-pressure opening and high pressure opening, and lower mandible portion 48 is for reducing the pressure in the plunger cavity between high pressure opening and low-pressure opening.This is illustrated by arrow 86 and 88, and this arrow illustrates from or go to the supply flow of PRV82.Therefore, a supply flow flows to a plunger cavity by upper mouth 46 from PRV82, and a supply flow flows to PRV82 by lower mandible portion 48 from a plunger cavity.For plunger cavity is connected with 48 with mouth 46, a control opening other, that lead to corresponding plunger cavity or conversion opening are radially set respectively in cylinder body 52.At this, in Fig. 6, change opening 90 and lead to plunger cavity 62, and conversion opening 92 leads to plunger cavity 64.
Fig. 6 additionally illustrates cylinder body 52 with plan view.At this, can see a plurality of columned plunger cavities 94, configure respectively a conversion opening 96 to described plunger cavity, described conversion opening is illustrated by a dotted line.
Fig. 6 illustrates piston engine, in this piston engine, lower plunger 68 be disposed generally on its upper dead center (English is: in region Top Dead Center) and upper plug 66 be arranged in its lower dead centre (English be: in region Bottom Dead Center).
For plunger cavity is connected with PRV82, conversion opening 96 intersects with mouth 46 or 48., in the side of spin axis 60, look up, conversion opening 96 and mouth 46 or 48 are shown greatly identical height and are arranged for this reason.At this, mouth 46 and 48 is configured to hole or gap, and their sections ground extends along the circle in the circumferential direction at bearing housing 50.In order to make the low pressure of plunger cavity 94 and piston engine-be connected with high pressure opening, control opening, wherein the control opening 98 of plunger cavity 62 shown in Figure 6 and the control opening 100 of plunger cavity 64 to each one of plunger cavity 94 configuration.Described control opening with respect to plunger cavity 62 or 64, roughly coaxially extend respectively and lead to cylinder body 52 swash plate dorsad 74 distolateral 102 on.
At this, preferably design like this geometrical shape of mouth 46,48 and conversion opening 96, PRV82 is loaded or unloaded corresponding to the first embodiment.
Disclose a kind of hydrostatic plunger machine, particularly axial piston engine, it has a plurality of plunger cavities, and plunger moves back and forth in described plunger cavity.At this, corresponding plunger cavity can alternately be connected with high pressure opening with low-pressure opening respectively by controlling opening.Between low-pressure opening and high pressure opening, be provided with transition region, corresponding plunger cavity moves in the transition part between low-pressure opening and high pressure opening by described transition region.In corresponding transition region, be provided with mouth, when one of the control opening at piston engine this plunger cavity in service and mouth intersect, corresponding plunger cavity is connected with memory cell (PRV) by described mouth.
Claims (14)
1. hydrostatic plunger machine, particularly an axial piston engine, have at least one plunger cavity (94), is furnished with movable plunger (66,68) in described plunger cavity, and described plunger cavity (94) can be by controlling opening (16; 98,100) alternately with low-pressure opening and the high pressure opening (2 of controlling component (1), 4) connect, between described low-pressure opening and described high pressure opening (2,4), be provided with two transition regions (18,20), it is characterized in that, in corresponding transition region (18,20), be provided with the mouth (22,24 for being connected with described plunger cavity; 46,48), described mouth is respectively by pressure piping (26,28; 80,84) with memory cell (30; 82) connect.
2. piston engine according to claim 1 wherein, is configured with dead center volume in described plunger cavity (94), and described memory cell (30; 82) described in storage volume ratio, dead center volume is much bigger.
3. piston engine according to claim 2, wherein, described storage volume is at least about 7.5 times of described dead center volume.
4. according to piston engine in any one of the preceding claims wherein, wherein, described control opening (16; 98,100), described low-pressure opening and high pressure opening (2,4) and described mouth (22,24; 46,48) constructed as follows, made at described plunger cavity (94) and corresponding mouth (22,24; 46,48), while connecting, control accordingly opening (16; 98,100) do not connect with described low-pressure opening and high pressure opening (2,4).
5. according to piston engine in any one of the preceding claims wherein, wherein, described mouth has different opening transverse incisions.
6. according to piston engine in any one of the preceding claims wherein, wherein, described mouth (22,24; 46,48) constructed as follows, made when crossing at described memory cell (30; 82) and between described plunger cavity, exchange the hydraulic medium volume flowrate of maximum possible.
7. according to piston engine in any one of the preceding claims wherein, wherein, described mouth (22,24; 46,48) and/or described control opening (16; 98,100; 90,92) designed as follows, made at described control opening (16; 98,100) after no longer connecting with described low-pressure opening or high pressure opening (2,4), corresponding mouth (22,24; 46,48) be connected with described plunger cavity (94) as early as possible.
8. according to piston engine in any one of the preceding claims wherein, wherein, described mouth and/or described control opening (16; 98,100) designed as follows, make pressure in the described memory cell and with described mouth (22,24; 46,48) pressure in the plunger cavity (94) connecting almost during balance, separates described mouth (22,24; 46,48) connection and between described plunger cavity (94).
9. according to piston engine in any one of the preceding claims wherein, wherein, radially from the spin axis of described piston engine, at least one mouth (22,24) at described low-pressure opening and/or high pressure opening (2,4) outside maximum outside diameter, be configured in described controlling component (1), and the control opening (16) of described plunger cavity has the cutout portion (32) being positioned at outside described external diameter.
10. piston engine according to claim 9, wherein, described cutout portion (32) in the circumferential direction of described control opening (16), be configured in about middle of described control opening, be particularly configured to u shape and in the circumferential direction of described control opening than described control opening much shorter.
11. according to piston engine in any one of the preceding claims wherein, and wherein, described mouth is configured to slot-shaped or microscler poroid and extend in circumferential direction with respect to the spin axis of described piston engine.
12. according to piston engine in any one of the preceding claims wherein, wherein, and described mouth (22,24; 46,48) there is respectively different opening transverse incisions.
13. according to piston engine in any one of the preceding claims wherein, wherein, described mouth (46,48) be configured in the bearing housing (50) of the cylinder body (52) with described plunger cavity (94), and described plunger cavity (94) is except described control opening (98,100) outside, also there is the control opening (90,92) can be alternately connecting with described mouth (46,48).
14. piston engines according to claim 13, wherein, additional described control opening (96) is in being arranged in the radial direction described cylinder body (52).
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE201110117081 DE102011117081A1 (en) | 2011-10-27 | 2011-10-27 | Hydrostatic piston machine |
| DE102011117081.6 | 2011-10-27 | ||
| PCT/EP2012/070103 WO2013060576A1 (en) | 2011-10-27 | 2012-10-11 | Hydrostatic piston machine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN103958893A true CN103958893A (en) | 2014-07-30 |
| CN103958893B CN103958893B (en) | 2016-09-28 |
Family
ID=47016712
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201280058300.4A Expired - Fee Related CN103958893B (en) | 2011-10-27 | 2012-10-11 | Hydrostatic piston engine |
Country Status (4)
| Country | Link |
|---|---|
| EP (1) | EP2771571A1 (en) |
| CN (1) | CN103958893B (en) |
| DE (1) | DE102011117081A1 (en) |
| WO (1) | WO2013060576A1 (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105605024A (en) * | 2014-11-14 | 2016-05-25 | 丹佛斯有限公司 | Hydraulic machine, in particular a hydraulic pressure exchanger |
| CN106232987A (en) * | 2014-08-01 | 2016-12-14 | 川崎重工业株式会社 | Hydraulic rotary machine |
| CN112483344A (en) * | 2019-09-10 | 2021-03-12 | 罗伯特·博世有限公司 | Hydrostatic piston engine unit |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| BR112012027692A2 (en) | 2010-04-29 | 2016-08-16 | Prad Res & Dev Ltd | method for obtaining gain corrected measurements, apparatus for determining a formation property of an underground formation, shielding for an in-pit profiling tool, and method for obtaining an impedance matrix using a substantially non-rotating in-pit tool |
| EP3591224A1 (en) * | 2018-07-05 | 2020-01-08 | Dana Motion Systems Italia S.R.L. | Piston hydraulic device |
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|---|---|---|---|---|
| US5247869A (en) * | 1991-09-06 | 1993-09-28 | Voac Hydraulics I Trollhattan Ab | Method and a device for damping flow pulsations in hydrostatic hydraulic machines of the displacement type |
| CN1146793A (en) * | 1995-02-10 | 1997-04-02 | 大金工业株式会社 | Variable displacement piston machine for reducing noise and vibration by reducing pulsation of discharge fluid |
| US6116871A (en) * | 1997-02-17 | 2000-09-12 | Linde Aktiengesellschaft | Device to reduce pulsations on a hydrostatic positive displacement unit |
| EP2324245A1 (en) * | 2008-09-08 | 2011-05-25 | Robert Bosch GmbH | Hydrostatic piston engine having a pulsation reduction device |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3956969A (en) * | 1974-12-09 | 1976-05-18 | Caterpillar Tractor Co. | Hydrostatic pump including separate noise reducing valve assemblies for its inlet and outlet pressure ports |
| JP2606758Y2 (en) * | 1992-12-22 | 2001-01-09 | 株式会社小松製作所 | Hydraulic pump / motor cylinder chamber pressure control device |
| DE19818721A1 (en) * | 1998-04-27 | 1999-10-28 | Mannesmann Rexroth Ag | Hydrostatic machine |
-
2011
- 2011-10-27 DE DE201110117081 patent/DE102011117081A1/en not_active Withdrawn
-
2012
- 2012-10-11 EP EP12772109.0A patent/EP2771571A1/en not_active Withdrawn
- 2012-10-11 CN CN201280058300.4A patent/CN103958893B/en not_active Expired - Fee Related
- 2012-10-11 WO PCT/EP2012/070103 patent/WO2013060576A1/en active Application Filing
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5247869A (en) * | 1991-09-06 | 1993-09-28 | Voac Hydraulics I Trollhattan Ab | Method and a device for damping flow pulsations in hydrostatic hydraulic machines of the displacement type |
| CN1146793A (en) * | 1995-02-10 | 1997-04-02 | 大金工业株式会社 | Variable displacement piston machine for reducing noise and vibration by reducing pulsation of discharge fluid |
| US6116871A (en) * | 1997-02-17 | 2000-09-12 | Linde Aktiengesellschaft | Device to reduce pulsations on a hydrostatic positive displacement unit |
| EP2324245A1 (en) * | 2008-09-08 | 2011-05-25 | Robert Bosch GmbH | Hydrostatic piston engine having a pulsation reduction device |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106232987A (en) * | 2014-08-01 | 2016-12-14 | 川崎重工业株式会社 | Hydraulic rotary machine |
| CN106232987B (en) * | 2014-08-01 | 2018-06-29 | 川崎重工业株式会社 | Hydraulic rotary machine |
| CN105605024A (en) * | 2014-11-14 | 2016-05-25 | 丹佛斯有限公司 | Hydraulic machine, in particular a hydraulic pressure exchanger |
| CN112483344A (en) * | 2019-09-10 | 2021-03-12 | 罗伯特·博世有限公司 | Hydrostatic piston engine unit |
Also Published As
| Publication number | Publication date |
|---|---|
| CN103958893B (en) | 2016-09-28 |
| DE102011117081A1 (en) | 2013-05-02 |
| WO2013060576A1 (en) | 2013-05-02 |
| EP2771571A1 (en) | 2014-09-03 |
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