EP3596310A1 - Axialkolbenmotor, kreisprozessvorrichtung, antriebseinheit und kraftfahrzeug - Google Patents
Axialkolbenmotor, kreisprozessvorrichtung, antriebseinheit und kraftfahrzeugInfo
- Publication number
- EP3596310A1 EP3596310A1 EP18712810.3A EP18712810A EP3596310A1 EP 3596310 A1 EP3596310 A1 EP 3596310A1 EP 18712810 A EP18712810 A EP 18712810A EP 3596310 A1 EP3596310 A1 EP 3596310A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- fluid
- inlet
- axial piston
- sealing element
- rotary valve
- 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
- 238000007789 sealing Methods 0.000 claims abstract description 107
- 239000012530 fluid Substances 0.000 claims abstract description 94
- 238000002485 combustion reaction Methods 0.000 claims description 18
- 239000000463 material Substances 0.000 claims description 9
- 238000000034 method Methods 0.000 claims description 9
- 230000008569 process Effects 0.000 claims description 9
- 238000004891 communication Methods 0.000 claims description 3
- 230000008016 vaporization Effects 0.000 claims 1
- 230000008859 change Effects 0.000 abstract description 6
- 238000013461 design Methods 0.000 description 5
- 239000007789 gas Substances 0.000 description 5
- 239000002918 waste heat Substances 0.000 description 5
- 239000007788 liquid Substances 0.000 description 4
- 238000003825 pressing Methods 0.000 description 4
- 238000010586 diagram Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 238000001704 evaporation Methods 0.000 description 3
- 230000008020 evaporation Effects 0.000 description 3
- 239000004810 polytetrafluoroethylene Substances 0.000 description 3
- 229920001343 polytetrafluoroethylene Polymers 0.000 description 3
- 238000012545 processing Methods 0.000 description 3
- 238000000926 separation method Methods 0.000 description 3
- 238000011144 upstream manufacturing Methods 0.000 description 3
- 229910000831 Steel Inorganic materials 0.000 description 2
- 239000002826 coolant Substances 0.000 description 2
- 238000001816 cooling Methods 0.000 description 2
- 239000000446 fuel Substances 0.000 description 2
- 230000010354 integration Effects 0.000 description 2
- 238000013021 overheating Methods 0.000 description 2
- 239000010959 steel Substances 0.000 description 2
- 238000012546 transfer Methods 0.000 description 2
- OKTJSMMVPCPJKN-UHFFFAOYSA-N Carbon Chemical compound [C] OKTJSMMVPCPJKN-UHFFFAOYSA-N 0.000 description 1
- RYGMFSIKBFXOCR-UHFFFAOYSA-N Copper Chemical compound [Cu] RYGMFSIKBFXOCR-UHFFFAOYSA-N 0.000 description 1
- 239000003990 capacitor Substances 0.000 description 1
- 229910052799 carbon Inorganic materials 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 239000011248 coating agent Substances 0.000 description 1
- 238000000576 coating method Methods 0.000 description 1
- 230000000295 complement effect Effects 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 229910052802 copper Inorganic materials 0.000 description 1
- 239000010949 copper Substances 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 125000004122 cyclic group Chemical group 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 230000008092 positive effect Effects 0.000 description 1
- 238000005381 potential energy Methods 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
- F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F01B3/0032—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
- F01B3/0044—Component parts, details, e.g. valves, sealings, lubrication
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
- F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F01B3/0032—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
- F01B3/0044—Component parts, details, e.g. valves, sealings, lubrication
- F01B3/0047—Particularities in the contacting area between cylinder barrel and valve plate
Definitions
- the invention relates to an axial piston motor and a cycle device with such, used in the cycle processing device as an expansion device axial piston motor.
- the invention further relates to a drive unit for a
- Integrated steam cycle process device The heat energy transferred in the heat exchanger from the exhaust gas to a working medium of the steam cycle device is partially converted into mechanical energy in an expansion device which can be used, for example, to assist the propulsion of a motor vehicle or to generate electrical energy. Downstream of the expansion device, the working medium is cooled in a second heat exchanger, the condenser, where it condenses. About a pump, an increase in pressure of the working fluid and its supply to the evaporator.
- an axial piston motor can be used, as is known from DE 10 2010 052 508 A1.
- Axial piston engines have a cylinder housing in which a plurality of cylinders are formed in an annular arrangement. In each of the cylinders, a piston is movably guided, wherein a phase offset is provided in the piston positions, based on a movement cycle of the piston ("piston cycle": OT->UT-> OT or
- UT-> OT-> UT which corresponds to the division between the cylinders.
- a pressurized fluid is sequentially introduced into the cylinders to apply a power stroke (OT-> UT) to each piston.
- the fluid causes movement of the respective piston and optionally expands (in a pneumatic axial piston motor).
- UT-> OT discharge stroke
- Movements of the pistons are transmitted via an obliquely arranged to the longitudinal axes of the cylinder plate to which the pistons are connected directly or via connecting rods, to an output shaft.
- Axial piston compressors and axial piston pumps have one in comparison to
- Axial piston motors of substantially identical construction wherein a mechanical drive power transmitted from the shaft via the obliquely arranged plate on the piston, while a rotational movement of the shaft or an associated drive motor is translated into the cyclic movement of the piston.
- a working stroke (UT-> OT) of each piston is a previously during a
- Axial piston machines (axial piston motors and axial piston compressors or pumps) are regularly executed in one of three designs.
- the cylinder housing rotates together with the piston.
- the shaft is arranged parallel to the cylinder housing and rotatably connected thereto. The movement of the piston controlling, swash plate is fixed.
- the cylinder housing does not rotate with the pistons guided therein.
- the swash plate is rotatably mounted on a swash plate, wherein the bearing surface of the swash plate and thus the orientation of the swash plate is aligned obliquely with respect to the longitudinal axes of the cylinder.
- the swash plate is rotatably connected to the shaft.
- the inlet and outlet valves of axial piston machines are regularly formed in the form of one or more rotary slide valves (see DE 10 201 1 1 18 622 A1 and DE 10 2015 204 367 A1), each of which comprises a rotary slide connected in rotation with the drive or driven shaft, depending on the particular
- the fluid-technical separation between the high-pressure side and the low-pressure side is of particular importance in order to prevent an overflow of the fluid from the inlet to the
- the invention had the object of providing an axial piston motor, which is characterized by a good fluidic separation between the high pressure side and the
- an axial piston motor according to claim 1.
- a cycle device having such an axial piston motor used as an expansion device, a drive unit for a motor vehicle having such
- Circular processing apparatus and a motor vehicle with such a drive unit are subject matters of claims 8 to 10.
- an axial piston motor is provided with a cylinder housing in which a plurality of cylinders are formed.
- pistons are movably guided, the pistons being connected to a swash plate, and a flow of fluid entering and exiting the cylinders via an inlet into the axial piston motor being controlled by means of inlet and outlet valves.
- the intake and exhaust valves formed in a cylinder head plate
- Fluid change ports (intake and / or exhaust ports, where combined intake and outlet openings are possible and preferably provided), which can be temporarily released and covered by means of a rotary valve.
- the rotary valve has a fluid-communicable with the fluid exchange openings in fluid-conducting connection
- Inlet opening which (ao) is in fluid communication with the inlet of the Axialkolbenmotors via a tubular sealing element, wherein the sealing element is acted upon by means of the inlet pressure of the fluid against an abutment to a formed between the sealing element and the abutment gap, in particular one to be sealed Connection between the high pressure side of the axial piston engine comprising the inlet and the one outlet of the axial piston engine
- Low pressure side represents, seal.
- inlet pressure is meant a pressure of the fluid which it has before entering the cylinders and in particular within the inlet.
- Axial piston motor is operated. As a result, an ever sufficient sealing effect can be achieved with each actual height of the inlet pressure of the fluid, wherein at the same time an excessively high contact pressure is avoided, because at a relatively low inlet pressure of the fluid, only a relatively smaller one
- Axialkolbenmotors may be relatively movable with respect to the sealing element produced.
- An inventive axial piston motor is preferably according to the
- the swash plate is rotatably mounted on a swash plate, wherein the support surface of the swash plate and thus the orientation of the swash plate are aligned obliquely with respect to the longitudinal axes of the cylinder.
- the swash plate is rotatably or at least rotationally connected to a (output) shaft connected.
- the rotary valve is the abutment, so that the Sealing element rotatably arranged with respect to the rotary valve and by means of
- Inlet pressure of the fluid is applied to the rotary valve. This allows a constructive advantageous integration of the sealing element can be achieved in the axial piston motor.
- Axial piston motor can also be provided that the sealing element is designed so deformable in the radial direction (preferably elastic) that an outer circumferential surface of the tubular sealing element is acted upon by the inlet pressure of the fluid against a contact surface of a cylinder head housing of the axial piston motor, whereby an advantageous sealed integration of the sealing element can be achieved in the cylinder head housing.
- Sealing element in particular rotatably connected to the rotary valve.
- Axial piston motor can be provided that the sealing element and the abutment (preferably in the form of the rotary valve) form a labyrinth seal, whereby even with a relatively low contact pressure (and correspondingly low
- Friction resistance a sufficiently good sealing effect can be realized.
- the sealing element forms a circumferential projection which engages in a circumferential recess of the abutment and / or the abutment forms a circumferential projection which engages in a circumferential recess of the sealing element.
- At least the surface of the sealing element and / or the abutment which forms the gap to be sealed is formed from a plain bearing material (eg PTFE).
- a plain bearing material eg PTFE
- the entire sealing element is formed from such a plain bearing material.
- plain bearing material is generally understood a material whose primary function is to achieve the lowest possible coefficient of friction in combination with the material of the contact partner.
- the sealing element can be combined in a particularly advantageous manner with a rotary valve which can be used to cover, as required, both inlet openings and outlet openings assigned to the cylinders (in particular also in the case of combined inlet and outlet openings)
- Outlet openings is provided and for this purpose a cavity is formed, wherein in this cavity a (preferably centrally with respect to the axis of rotation of the
- Form through holes which connect at a coverage (each) of a cylinder associated fluid exchange opening the corresponding cylinder with preferably the outlet of the axial piston motor.
- Axial piston motor can be provided that the longitudinal axis of the tubular sealing element is arranged coaxially with respect to the axis of rotation of the rotary valve. This can be achieved in an advantageous manner that the relative movement between the sealing element and the abutment is limited to a relative rotation.
- a (steam) cycle process device comprises a circuit for a fluid (working medium), in which circulation
- an evaporator i.e., a first heat exchange device provided for supplying heat energy into the fluid
- a first heat exchange device provided for supplying heat energy into the fluid
- a condenser i.e., a second heat exchange device provided for dissipating heat energy from the fluid
- a condenser provided for condensing the fluid
- a conveying device (in particular a pump) for conveying the fluid
- the expansion device is designed in the form of an axial piston motor according to the invention.
- the invention further relates to a drive unit for a motor vehicle, which comprises at least one internal combustion engine, a combustion engine and a
- the drive unit further comprises a circuit process device according to the invention, wherein the evaporator is provided and adapted to heat energy of
- the invention also relates to a motor vehicle comprising such a drive unit according to the invention, wherein the internal combustion engine of the drive unit can be provided in particular for generating a traction drive power for the motor vehicle.
- the motor vehicle may in particular be a wheel-based motor vehicle (preferably a car or a truck). A use with others
- Fig. 1 an embodiment of an axial piston motor according to the invention (only in
- Fig. 2 the axial piston motor in a longitudinal section
- Fig. 4 the rotary valve of the axial piston motor in a perspective
- Fig. 7 a cross section through the rotary disk along the plane VII - VII in the
- Fig. 5; 8 shows a second radial section through the rotary valve
- FIG. 10 shows a circuit process device according to the invention in a schematic
- FIG. 11 a T-S diagram belonging to a Clausius-Rankine process which can be carried out by means of the cycle-processing device.
- FIG. 11 a T-S diagram belonging to a Clausius-Rankine process which can be carried out by means of the cycle-processing device.
- Figs. 1 to 9 show an embodiment of an inventive
- Axialkolbenmotors 10 This is designed in a swash plate type and includes a multi-part cylinder housing 12, which comprises a plurality (here: six) of parallel aligned cylinder tubes 14.
- the cylinder tubes 14 define cylinders 16, in each of which a piston 18 is movably guided.
- the pistons 18 are each connected via a connecting rod 20 to an annular swash plate 22.
- the swash plate 22 is rotatably mounted on a swash plate 24 which is rotatably connected to a (output) shaft 26 of the axial piston 10.
- the swash plate 22 and the swash plate 24 have (coaxial) longitudinal axes 28 which extend at a defined angle greater than zero to the longitudinal axes 30, 32 of the shaft 26 and the cylinder 16 inclined.
- Cylinder head 36 near top dead center (TDC) and a bottom dead center (UT) remote from the cylinder head 36.
- the piston-cylinder units work with two cycles. The movement of each piston 18 from the TDC to the TDC is effected by the fluid flowing into the respective cylinders 16 (working stroke of the respective cylinder 16 and working stroke of the respective piston 18). In the guided by the swash plate 22 movement of the piston 18 from the UT to the TDC is the during the
- Timing is controlled by the cylinders 16 associated intake and exhaust valves, which are in the form of a combined rotary valve 38.
- the rotary slide valve 38 comprises a cylinder head plate 40 which abuts the cylinder housing 12 sealingly on the front side on the side remote from the swash plate 22.
- the cylinder head plate 40 has one each as a combined input and
- Further openings 44 are used to receive screws 46 through which a cylinder head housing 48, the cylinder head plate 40, the cylinder housing 12 and a surrounding the swash plate 22 and the swash plate 24 housing 50 are interconnected.
- a rotary valve 52 is arranged which is non-rotatably connected to the shaft 26 and thus during operation of the axial piston 10 relative to the
- Cylinder head plate 40 alternately and once per revolution of the shaft 26 in
- the gaseous fluid is supplied via a cavity 60 integrated in the rotary valve 52 and via a fluid channel 62 connecting the cavity 60 with the inlet opening 54 (see Fig. 8).
- the fluid is expelled from the respective cylinders 16 and discharged through an outlet 64 from the axial piston 10.
- the length of the inlet opening 54 of the rotary valve 52 (with respect to the intended direction of rotation 72 of the Rotary valve 52) selected such that an overlap with always only the
- Fluid change port 42 of a single cylinder 16 is given, while the significantly longer outlet opening 56 of the rotary valve 52, a simultaneous release of several fluid change openings 42 provides.
- the sealing element 98 serves a fluid-conducting connection between the inlet 58 and the cavity 60 (and via this cavity 60 with the inlet opening 54), wherein the sealing element 98, an overflow of introduced via the inlet 58 in the axial piston 10 from the high pressure side of the axial piston 10th , which corresponds to the fluid guide between the inlet 58 and the inlet opening 54 of the rotary valve 52, to the low pressure side of the axial piston motor 10, which also integrated in the cylinder head 36 fluid guide between the outlet opening 56 of the
- Rotary valve 52 and the outlet 64 of the axial piston motor 10 corresponds to prevent as much as possible.
- the problem here is the rotation of the rotary valve 52 relative to the cylinder head housing 48 during operation of the Axialkolbenmotors 10, so that by means of the sealing element 98 a fluidic separation of the high pressure side and the low pressure side of the axial piston 10 is to be achieved in the best possible manner despite this relative rotation.
- the tubular sealing element 98 whose longitudinal axis 32 (as well as the longitudinal axis 32 of the inlet 58) is arranged coaxially with respect to the axis of rotation 32 of the rotary valve 52, is largely immovably received within the cylinder head housing 48 and the
- Rotary slide 52 thus also rotates relative to the sealing element 98 during operation of the axial piston motor 10. Specifically, there is a sliding relative movement between one of the annular end faces of the sealing element 98 and the adjoining portion of the top of the rotary valve 52, as can be seen in particular from FIG. 3.
- Fig. 3 shows an enlarged view of the marked in Fig. 2 with III section, wherein in addition also arrows are drawn in Fig. 3, symbolize the forces that result from the fact that the sealing element 98 by means of
- sealing element 98 is acted upon in the longitudinal axial direction by the inlet pressure of the fluid against the top of the rotating 52 during rotation of the Axialkolbenmotors 10 relative to the sealing member 98 rotary valve, whereby moreover an overflow of fluid in the region of the transition between the inner volume of the sealing element and the Cavity 60 of the rotary valve 52 via the formed there between the sealing element 98 and the rotary valve 52, annular circumferential gap is largely prevented.
- the sealing element 98 in combination with the rotary valve 52 forms a labyrinth seal, for which at the top of the rotary valve 52, an annular circumferential projection 102 is formed, which in a complementary recess in the front side of Sealing element 98 engages. Furthermore, the sealing element 98 also forms on the end face facing the rotary slide 52 radially inwardly an annular circumferential projection 104, which engages in a connection opening 106 which is integrated into the upper side of the rotary slide 52 and opens into the cavity 60 of the rotary slide 52.
- the force with which the sealing element 98 against the Rotary slide 52 is pressed results from the height of the inlet pressure of the fluid and the difference in the size of the inlet 58 facing (larger) end face of the sealing member 98 on the one hand and the size of that (smaller) portion of the rotary valve 52 facing end face of the sealing element 98th from the into the connection opening 106 of the
- Rotary slide 52 projecting projection 104 is formed, on the other hand.
- the inlet 58 of the sealing element 98 facing the inlet 58 is designed such that a free space 34 is formed adjacent to this end face of the sealing element 98, in which the diameter of the cylindrical inlet 58 Outer diameter of the sealing element 98 corresponds.
- the sealing member 98 is formed of a plain bearing material (e.g., PTFE).
- PTFE a plain bearing material
- the sealing element 98 is subject to wear due to the relative movement with respect to the rotary valve 52.
- this wear can automatically due to the leksaxial displaceable mounting of the sealing element 98 in the cylinder head housing 48 and an adapted dimensions the sealing element 98 and the
- Rotary valve 52 in particular with respect to the interlocking projections 102, 104, in combination with the longitudinal axial loading of the sealing element 98 by means of the inlet pressure of the fluid compensate.
- the rotary valve 52 and concretely a base body 66 of the rotary valve 52 is designed for a manufacturing technology advantageous embodiment of the cavity 60 in several parts.
- This comprises a base part 68, which forms a central receiving recess into which a cover part 78 is inserted.
- the cover part 78 delimits the cavity 60 with the upper side of the base part 68 in the region of the receiving recess, wherein an opening in the lateral surface of the cover part 78 allows a fluid-conducting connection between the cavity 60 and the fluid channel 62.
- the rotary valve 52 comprises, in addition to the main body 66 a via a
- this sealing plate 70 is the
- Inlet opening 54 of the rotary valve 52 is formed.
- the closed (i.e., not forming the inlet opening 54) portions of the sealing plate 70 serve a need-covering the fluid exchange openings 42, wherein at least in the direction of rotation 72 of the rotary valve 52 behind the inlet opening 54 located portion due to the rotationally fixed coupling of
- Rotary slide 52 is always arranged on the swash plate 24 via the shaft 26 so that it is arranged in the region of those three cylinders 16, in which the associated piston 18 currently perform a power stroke during operation of the axial piston motor 10.
- the sealing plate 70 is movably arranged in a (partial) annular receiving recess, which is formed by the underside of the base body 66 adjoining the cylinder head plate 40, one possible over a relatively small distance Displacement of the sealing plate 70 in the direction parallel to the axis of rotation 32 of the rotary valve 52 directions and thus on the cylinder head plate 40 to or from this is possible.
- This makes it possible to press the sealing plate 70 to the cylinder head plate 40 as needed, whereby the fluid exchange openings 42 covered by the closed portion of the sealing plate 70 are not only covered, but also the gap formed between this portion of the sealing plate 70 and the cylinder head plate 40 due to a sufficiently high Force with which the sealing plate 70 is pressed against the cylinder head plate 40 is sufficiently sealed.
- the underside of the main body 66 in a defined, relatively small (for example, about 3/10 mm) distance to the top of the
- Friction losses are maintained when the selection of the materials of which the cylinder head plate 40 (e.g., steel) and the seal plate 70 (e.g., copper) are formed are also selected for the lowest possible coefficient of friction. Furthermore, there is the possibility of coating the cylinder head plate 40 and / or the sealing plate 70 with a plain bearing material (e.g., PTFE or DLC (Diamond-like Carbon)). Among other things, the sealing plate 70 may advantageously be formed of steel.
- a plain bearing material e.g., PTFE or DLC (Diamond-like Carbon
- Cavity 60 is. For a sealing of the circumferential gap between the
- receiving receiving openings each have a sealing ring 80 (O-ring) is provided.
- the pressurizing pistons 74 which are acted upon by the inlet pressure of the fluid, press the sealing plate 70 against the cylinder head plate 40, thereby achieving the previously described sealed covering of the fluid changing openings 42 of those cylinders 16 whose associated pistons 18 perform a working stroke.
- the force with which the sealing plate 70 is pressed against the cylinder head plate 40 directly dependent on the height of the inlet pressure of the fluid, so that at each provided during operation of the axial piston motor 10 height of the inlet pressure on the one hand
- Cylinder head plate 40 is avoided.
- a closed section upstream of the inlet opening 54 is provided, whose length in the circumferential direction corresponds at least to the width of the fluid exchange openings 42 in the circumferential direction (cf., in particular, FIG. This ensures that even with only an initial overlap of the inlet opening 54 of the sealing plate 70 with the individual fluid exchange openings 42 of the cylinder head plate 40, the entire fluid flowing into the respective cylinder 16 remains therein and does not flow out of the sealing plate 70 initially formed gap again , Also in this upstream of the inlet opening 54 a pressing of the sealing plate 70 by means of a pressure piston 74 is provided (see Fig .. 5). About a variation of the length of this the inlet opening 54 upstream,
- a pressure piston 74 is provided immediately behind (with respect to the direction of rotation 72) of the inlet opening 54, which is followed by a plurality of further pressure piston 74. It is provided that on the one hand, the surfaces of the inlet pressure of the fluid exposed upper sides of the pressure piston 74 are formed in the direction of rotation 72 and on the other hand, the distances between the pressure piston 74th are formed smaller in the direction of rotation, whereby a particularly strong pressing of the sealing plate 70 to the cylinder head plate 40 in a region encompassing the inlet opening 54 is achieved, while the contact pressure with increasing distance from the inlet opening 54 is smaller, causing the generated by the individual pressure piston 74 and pressure forces acting on different areas of the sealing plate 70 are adapted to the fluid pressure progressively decreasing during the working cycles in the cylinders 16.
- Taumelinfußes 24 is taken, is provided, this against a
- Secured sleeve 82 is provided, which is connected to the cylinder housing 12.
- the securing sleeve 82 is also connected via a cardan-like joint arrangement with the
- the joint arrangement rotatably binds the swash plate 22 to the locking sleeve 82 and thus to the cylinder housing 12 and at the same time allows the tumbling movement of the swash plate 22.
- the joint arrangement comprises a joint ring 84, which is rotatably connected to the locking sleeve 82 about a first axis via two respective bearing pins 86 and to the swash plate 22 about a second axis perpendicular to the first axis.
- the axial piston motor 10 can be used, for example, in a cycle device 88 for utilizing waste heat of an internal combustion engine 90 of an internal combustion engine of a motor vehicle (compare FIG. 10).
- a vaporized and superheated and pressurized fluid expands in the axial piston motor 10, whereby a part of the thermal and potential energy of the fluid in mechanical energy or power (P me c h ) is converted.
- the fluid is conveyed in the liquid state by means of a pump 92 (conveying device) to an evaporator 94 in which it is heated by the transfer of heat energy from exhaust gas discharged from the internal combustion engine 90 via an exhaust gas line which integrates the evaporator 94.
- the thus vaporized and superheated fluid then flows to the
- Heat transfer to a cooling medium for example, in a the one
- Internal combustion engine 90 integrated cooling system of the motor vehicle flowing coolant, cooled.
- the fluid condenses, so that it can be re-supplied to the evaporator 94 in the liquid state by means of the pump 92. Due to the The liquid fluid is pumped by means of the pump 92 and compression of the fluid present in the gaseous state between the evaporator 94 and the axial piston motor 10 (expander) is also achieved to an intended operating pressure, the pressure being generated by the pump 92 interacting with the expansion of the gaseous fluid in the axial piston 10 is.
- the pressure level is approached adiabatically and isentropically to a defined value in accordance with the TS diagram of FIG. 11 (theoretically or idealized) and a defined volume flow is ensured.
- a (theoretical or idealized) isobaric heat supply with evaporation and overheating takes place.
- the evaporation begins, which is completed when the state point b "is reached, and from the state point b" to the state point c, the vaporous fluid is overheated.
- the aim of the consideration in the TS diagram is a maximization of the supplied heat from the state point b to the state point c and a reduction of the dissipated heat (q_ab) from the state point d to the state point a.
- the enclosed area from the state point a via the state points b and c to the state point d should be maximized in the intended temperature range.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Hydraulic Motors (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102017105609.2A DE102017105609A1 (de) | 2017-03-16 | 2017-03-16 | Axialkolbenmotor, Kreisprozessvorrichtung, Antriebseinheit und Kraftfahrzeug |
PCT/EP2018/055619 WO2018166867A1 (de) | 2017-03-16 | 2018-03-07 | Axialkolbenmotor, kreisprozessvorrichtung, antriebseinheit und kraftfahrzeug |
Publications (2)
Publication Number | Publication Date |
---|---|
EP3596310A1 true EP3596310A1 (de) | 2020-01-22 |
EP3596310B1 EP3596310B1 (de) | 2021-01-13 |
Family
ID=61763925
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP18712810.3A Active EP3596310B1 (de) | 2017-03-16 | 2018-03-07 | Axialkolbenmotor, kreisprozessvorrichtung, antriebseinheit und kraftfahrzeug |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP3596310B1 (de) |
DE (1) | DE102017105609A1 (de) |
WO (1) | WO2018166867A1 (de) |
Family Cites Families (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CH471317A (de) * | 1968-09-13 | 1969-04-15 | August Dr Monath | Kolbenmaschine |
US5799562A (en) * | 1996-03-13 | 1998-09-01 | Weinberg; Morgan W. | Regenerative braking method and apparatus therefor |
US7367783B2 (en) * | 2003-03-07 | 2008-05-06 | Honda Motor Co., Ltd. | Rotating fluid machine |
JP2005163582A (ja) * | 2003-12-01 | 2005-06-23 | Honda Motor Co Ltd | 回転流体機械 |
DE102009028467A1 (de) | 2009-08-12 | 2011-02-17 | Robert Bosch Gmbh | Vorrichtung zur Nutzung von Abwärme |
DE102010052508A1 (de) | 2010-11-26 | 2012-05-31 | Daimler Ag | Abwärmenutzungsvorrichtung |
DE102011118622B4 (de) | 2011-11-16 | 2017-06-29 | Mahle International Gmbh | Axialkolbenmaschine mit Auslasssteuerung |
DE102013213614A1 (de) * | 2013-07-11 | 2015-01-15 | Volkswagen Aktiengesellschaft | Axialkolbenmaschine |
DE102014209900A1 (de) * | 2014-05-23 | 2015-11-26 | Mahle International Gmbh | Axialkolbenmaschine |
DE102015204367A1 (de) | 2015-03-11 | 2016-09-15 | Mahle International Gmbh | Axialkolbenmaschine |
-
2017
- 2017-03-16 DE DE102017105609.2A patent/DE102017105609A1/de not_active Withdrawn
-
2018
- 2018-03-07 WO PCT/EP2018/055619 patent/WO2018166867A1/de unknown
- 2018-03-07 EP EP18712810.3A patent/EP3596310B1/de active Active
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EP3596310B1 (de) | 2021-01-13 |
WO2018166867A1 (de) | 2018-09-20 |
DE102017105609A1 (de) | 2018-09-20 |
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