• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    The invention relates to a rotary piston internal combustion engine (1) having at least one rotary piston (4) circulating in a chamber (3) of a housing (2), the chamber (3) being guided by a trochoidal running surface (5) in a central housing part (2a) and of formed on each side of the central housing part (2a) in the direction of the axis (10a) of the eccentric shaft (10) directly or indirectly lateral housing parts (2b, 2b) 2c), wherein at least one cooling channel arrangement (52, 53, 54) in the lateral first housing part (2b), in the central housing part (2a) and in the lateral second housing part (2c) of the piston internal combustion engine (1) of cooling liquid of a cooling circuit (50a) of a Cooling system (50) can be flowed through. In order to achieve the best possible heat dissipation in the simplest possible way, it is provided that a first piston-side cooling channel arrangement (52) of the lateral first housing part (2b), a central cooling channel arrangement (53) of the central housing part (2a) and a second piston-side cooling channel arrangement (54). of the lateral second housing part (2c) in the cooling circuit (50a) of the cooling system (50) are successively flowed through in the order given.
    公开号:AT510749A1
    申请号:T1912/2010
    申请日:2010-11-18
    公开日:2012-06-15
    发明作者:Aldo Dipl Ing Fh Bregant；Andreas Dipl Ing Fh Nimmervoll；Gernot Fuckar；Robert Berger
    申请人:Avl List Gmbh；
    IPC主号:
    专利说明:

    - 1 - 56088
    The invention relates to a rotary piston internal combustion engine having at least one circulating in a chamber of a housing rotary piston, wherein the chamber is formed by a trochoidenförmigen running surface in a central housing parts and spaced from each other, arranged normal to an eccentric shaft side treads, both sides of the central housing part in the direction the axis of the eccentric shaft directly or indirectly connect lateral housing parts, wherein at least one cooling channel arrangement in the lateral first housing part, in the central housing part and in the lateral second housing part of the reciprocating internal combustion engine of coolant a cooling circuit of a cooling system can be flowed through.
    The AT 505 950 Bl describes a power generator for range extension of an electric vehicle, with a rotary piston internal combustion engine and a generator which is arranged coaxially with the output shaft of the internal combustion engine. The internal combustion engine and the generator are arranged in a cooling-air flowed through housing and formed as a unit. The housing has in the region of the rotary piston of the rotary piston internal combustion engine on a central housing part which is bounded on both sides by lateral housing parts, wherein in each case a bearing for the eccentric shaft of the internal combustion engine is arranged in the lateral housing parts. On the generator side housing parts encloses a housing side of the generator and a final lid this part. The housing part of the generator and the cover part together span a cavity in which the stator and the rotor of the generator is arranged.
    From DE 10 2008 026 920 Al a rotary piston internal combustion engine is known, which consists essentially of a shell housing, an end side part, a driven side side part, a piston and an eccentric shaft, wherein the side parts each have a hub for receiving a main bearing, depending on a lateral track for the piston, each having a parallel to the raceways in the side parts arranged cooling water space with a water inlet opening and a water outlet opening and an oil chamber with a Ölausflussöffnung. The side parts are made in two parts and consist of bolted together Laufbahnteii and cover part. Each consisting of a cast iron material Laufbahnteii has a low-cost track for the piston, while the respective cover part is made of light metal casting and offers weight advantages.
    From DE 25 19 907 Bl is a rotary piston machine Trochoidenbauart with a limited within a two-sided side panels housing shell - 2 - located piston, the housing is constructed of disc-shaped parts, which are centered by dowel pins and held together by through bolts. To a the trochoidal piston barrel forming the central housing part close while flat cover plates and side housing parts, which receive the bearings for the eccentric shaft.
    Furthermore, DE 101 24 561 A1 discloses a trochoid-type rotary engine in which the side windows are composed of a side part produced as a cast part and a cover plate, the side part having a support function and the cover plates having only one sealing function. In the side part, a series of ribs are formed, which together with the cover plate form flow channels for a cooling liquid. A similar construction is known from US 3,280,802 A.
    From DE 36 01 193 Al an existing power generator and internal combustion engine unit is known, wherein the internal combustion engine and the generator have a common cooling water circuit, and wherein the coming of the generator, the generator heat laxative line is connected to the cooling water inlet of the internal combustion engine.
    DE 4 020 416 A1 describes a generator with armature shaft cooling, the generator and a drive motor formed by an internal combustion engine having a common cooling system.
    In a rotary piston internal combustion engine, in particular in a power generator, individual areas, components and components have different heat inputs and different optimal operating temperatures.
    It is the object of the invention to achieve in a simple manner a component-appropriate best possible heat dissipation.
    According to the invention, this is achieved by a first piston-side cooling channel arrangement of the lateral first housing part, a central cooling channel arrangement of the central housing part and a second piston-side cooling channel arrangement of the lateral second housing part in the cooling circuit of the cooling system in the order indicated are successively flowed through, preferably in the region of the first housing part or a coolant inlet entering the first housing part and a coolant outlet in the region of the second housing part or a cover part closing the second housing part.
    Especially with at least one coaxially with the eccentric shaft in the same housing as the rotary piston internal combustion engine arranged electrical Ma- - 3 - machine, which forms a power generator, in particular for range extension of an electric vehicle, forming unit with the rotary piston engine, thus all components, which have a lower operating temperature have as the piston internal combustion engine, are cooled in the cooling circuit in front of the piston internal combustion engine by the cool strand of the cooling system. In order to ensure sufficient cooling of the electrical machine, it is advantageous if, for cooling the electric machine, preferably in the lateral first housing part, an electro-sided cooling channel arrangement is arranged, which is arranged in the cooling circuit of the cooling system, wherein particularly preferably the cooling channel arrangements of the electric machine receiving side first housing part, the central housing part and the lateral second housing part in the cooling circuit can be flowed through successively.
    As viewed around the axis of the eccentric shaft, rotary piston internal combustion engines have a cold angular segment region of the housing in the inlet region and a hot angular segment region of the housing in the combustion and exhaust region. These two angular segment areas have different heat input and thus a different cooling requirement. To meet this, the cooling chambers are not arranged rotationally symmetrical about the axis of the eccentric shaft,
    The best possible heat removal from the chamber of the rotary piston engine containing the rotary piston can be achieved if the first piston-side cooling channel arrangement arranged in the region of a first side running surface forming the first side wall extends at least in an arcuate manner over an angle of at least 180 ° in a hot angular segment region of the rotary piston internal combustion engine first cooling channel, which is fluidly connected to the central cooling channel arrangement. It is particularly advantageous if the first piston-side cooling space arrangement has a separate from the first cooling channel, flow-connected to the central cooling channel arrangement arcuate second Kühlkanai in a cold angular segment region of the rotary piston internal combustion engine, preferably the second cooling chamber over an angular range between 60 ° to 120 °, especially preferably extends from 90 ° about the axis of the eccentric shaft.
    A particularly good cooling of the electric machine can be achieved if the electro-side cooling channel arrangement has at least one annular channel, preferably loop-shaped, in the inlet region of at least one cylindrical jacket region surrounding the electric machine of the first housing part. In order to be able to precisely tune the cooling of the hot angular segment region and the cold angular segment region of the internal combustion engine, it is particularly advantageous if the first cooling chamber and the second cooling chamber of the first piston-side cooling chamber arrangement are flow-connected to different regions of the annular channel.
    To achieve a uniform heat dissipation, it is particularly advantageous if the second housing part in the region of a second side wall forming the second guide surface has a second cooling chamber connected to the central cooling chamber arrangement second piston side cooling chamber arrangement, preferably the second piston side cooling chamber arrangement one, more preferably only a single hot Angular segment region of the rotary piston internal combustion engine arranged arcuate cooling channel which extends over an angular range of at least 180 °, preferably at least 225 °, more preferably by an angular range of at least 240 °, about the axis of the eccentric shaft.
    Calculations and tests have shown that the best results in terms of a uniform temperature distribution can be achieved when the first and second piston-side cooling chamber arrangement are different, preferably have different numbers of cooling chambers and / or the cooling chambers of the first cooling chamber arrangement and the second cooling chamber arrangement different Cover angular areas around the axis of the eccentric shaft.
    To account for different heat inputs and component temperatures of the electric machine and the internal combustion engine may further be provided in the invention that the electro-side cooling channel assembly and the first piston-side cooling arrangement are at least partially arranged in parallel in the cooling circuit of the cooling system, preferably guided by the loop-shaped annular channel and particularly preferably thereafter the second cooling channel supplied second cooling medium Ström is less than a directly the first piston-side cooling channel arrangement, preferably the first cooling channel supplied first coolant flow. In this case, after passing through the cooling channels in the hot angular segment region, the first coolant stream can merge with the second coolant stream after it has flowed through the cooling channels in the cold angular segment region in the region of the cooling channel of the second housing part. Simulations have shown that a particularly favorable temperature of the individual components can be achieved if the volume flow of the first coolant flow about 70% to 90%, preferably 80% to 88%, preferably, supplied to the housing and / or from the cooling channel of the second discharged lateral housing part, total coolant flow is. This allows for excessive cooling of the hot angle segment areas. - 5 -
    To save components, the side walls may be integrally formed with the first and second housing part. The weight and the manufacturing cost can be reduced and / or increase the life of the rotary piston internal combustion engine, when the first and / or the second side wall is formed by a arranged between the first and second housing part and the central housings seteii separate side plate, which preferably made a different material than the lateral first and second housing part or the central housing part. For example, the side plates made of steel, gray cast iron or ceramic and the housing parts are made of an aluminum die-cast.
    The lateral first housing part, the central housing part and the second housing part, preferably also at least one side plate, may be connected to each other by axially parallel fixing screws which pass through one of the two lateral housing parts, the central housing part and the side plates and are bolted to the other side ,
    In order to achieve particularly good heat dissipation, in particular in the region of the ignition location, at least one fastening screw arranged in the hot angular segment region can be made wet and penetrate an axially parallel cooling channel of the central cooling channel arrangement.
    The invention will be explained in more detail below with reference to FIGS.
    2 shows an electro-side cooling channel arrangement of the first housing part in a section along the line II - II, Fig. 3, the electro-side cooling chamber arrangement in a frontal view, Fig. 4 and 5, an electrical side cooling channel arrangement in each case an oblique view 6 the first housing part in an oblique view from the side of the cover part, FIG. 7 the first housing part in a further oblique view, FIG. 8 the first housing part in an oblique view from the side of the rotary piston, FIG. 9 a central housing part in one FIG. 10 a second housing part in a side view from the side of the rotary piston, FIG. 11 cooling system arrangements of the first housing part in a side view, FIG. 12 these cooling system arrangements of the first housing part in an oblique view, FIG. 13 a first piston-side cooling channel arrangement, FIG. 14 a second piston side Kühlkana 15 shows the cooling channel arrangements of the power generation unit in an oblique view, and FIG. 16 shows the detail XVI of the central coolant arrangement from FIG. 15.
    Fig. 1 shows a power generation unit 40 (range extender), in particular for range expansion of an electric vehicle, wherein in a housing 2 - 6 - a rotary piston internal combustion engine 1 and an example permanent-magnet electric machine 14 is arranged. The housing 2 has a chamber 3, in which a rotary piston 4 along a trochoidenförmigen running surface 5 of the housing 2 is arranged circumferentially. The chamber 3 is formed by the trochoidal tread 5 and by lateral treads 6, 7. The housing 2 has a trochoidal tread 5 forming the central housing part 2a, lateral housing parts 2b and 2c, preferably the central housing part 2a limiting side plates 8, 9, and a lateral housing part 2b limiting the lid part 2d.
    In each of the lateral housing parts 2b, 2c, an eccentric shaft 10, which is arranged in an inner housing space 15 and is driven by the rotary piston 4, is rotatably mounted via bearings 11, 12, which are designed, for example, as roller bearings. Shaft equal to the eccentric shaft 10 of the rotor 13 is formed in the same housing 2 arranged electrical machine. The bearing 11 receiving side first housing parts 2b has a bell-shaped, cylindrical shell portion 2b ', which spans a substantially cylindrical interior 15a, in which the rotor 13, and the stator 14a of the electric machine 14 is arranged. The cylindrical interior 15a is closed by a in Fig. 1 adjoining the housing part 2b lid part 2d.
    The electric machine 14 and the rotary piston internal combustion engine 1 have a common cooling system 50, wherein in the housing parts 2d, 2b, 2a and 2c provided cooling channel arrangements 51, 52, 53 and 54 are flowed through successively. Thus, in succession, the electric machine 14 and then the rotary piston internal combustion engine 1 are cooled. An annular electrosei-type cooling channel arrangement 51 may be partially formed by the cover part 2d and partially by the first housing part 2b.
    In the first housing part 2b, a number of arranged in the direction of the axis 10a of the eccentric shaft 10 cooling chambers 51a are arranged in the region of the electrical machine 14, which is fluidly connected to an annular space 51b in the region of the end face 33 of the first housing part 2b and / or the cover part 2d.
    2 to 5 show schematically an electro-side cooling channel arrangement 51 in the first housing part 2b, wherein the coolant inlet into the first housing part 2b is designated by reference numeral 55 and the coolant outlet by reference numeral 56. In order to demonstrate the flow path of the cooling liquid represented by the arrows, the coolant outlet 56 in FIG. 2 is turned downwards in the sectional plane. Although coolant inlet 55 and coolant outlet 56 are shown in FIG. 2 in the region of end face 33 in order to demonstrate the meandering coolant flow of loop-like cooling channel 51, a different position in jacket area 2b ', for example, is particularly important for coolant outlet 56 the rotary piston engine 1 facing end face 34 possible.
    In order to enable an optimal meandering coolant flow through the loop-like annular channel 51c in the cylindrical shell region 2b 'of the first housing element 2b surrounding the stator 14a and the rotor 13, deflection devices 57 are axially inserted into the initial regions of the cooling chambers 51a. which deflecting devices 57 may be formed, for example, by plugs 57a or guide ribs or the like. The deflection devices 57 are inserted, for example, in co-molded axial receptacles 37 of the first housing part 2b in the annular space 51b. Alternatively, it is also possible, the deflecting means 57 in the lid part 2d detachable or non-detachable - for example, by pouring - to order. By deflecting means 57, the coolant flowing in the circumferential direction is deflected in the direction of the axis 10a into the cooling chambers 51a and returned along the walls 51a 'back into the annular space 51b. As a result of this loop-like movement of the coolant, the cooling region of the first housing part 2b which is decisive for the electrical machine 14 is uniformly cooled, wherein a fine-tuning of the heat dissipation by changing the cross section and / or the length of the deflection devices 57 can take place. The deflection devices 57 may be formed, for example, by plastic plugs or the like.
    The cooling chambers 51a are essentially closed in the region of the end face 34, for example by casting, or by a cover part, so that a forced deflection takes place at the end of each cooling chamber 51a. In Fig. 5, flow lines of the refrigerant flow in the loop-like annulus 51c are shown. The deflection devices are only relatively small, ie by an extent which is approximately the axial extent of the annular space 51b, inserted into the cooling chambers 51a. As can be seen, this results in the cooling chambers 51a to flow separation and Verwirbelungserscheinungen, which can be improved in these areas of heat transfer.
    The deflection devices 57, which can be moved into the cooling channel arrangement 51, allow a meandering coolant flow in the first housing part 2b surrounding the electric machine 14, and thus the best possible heat dissipation, in a manner very simple in terms of production.
    In the rotary piston 4 facing end face 34 of the first housing part 2b, a first piston-side cooling channel arrangement 52 is formed, as shown in Fig. 8 - 8 - shows. The first piston-side cooling channel arrangement 52 consists of a kidney or arcuate first cooling channel 52a and a likewise kidney or arcuate second cooling channel 52b, the first cooling channel 52a being connected via connection openings 52a 'and 52a'. is fluidly connected to the electro-side cooling channel assembly 51. The second cooling channel 52b 'is also fluidly connected to the electro-side cooling channel arrangement 51 via a connection opening 52b1. The connection openings 52a ', 52a " on the one hand and 52b 'start from different areas of the annular electro-side cooling channel arrangement 51, so that the cooling liquid with different temperatures in the first and second cooling channel 52a, 52b occurs. The kidney-shaped first cooling channel 52a is arranged in a hot angular segment region H of the housing 2, that is to say in the region of the combustion and / or the outlet. The kidney-shaped second cooling channel 52b, however, is located in a cold angle segment region C of the housing 2, that is, for example, in the region of the inlet. The kidney or arcuate first cooling channel 52a extends over an angular range a of at least 180 °, for example 210 °, about the axis 10a of the eccentric shaft 10. The kidney-shaped or arcuate second cooling channel 52b, on the other hand, only clamps an angle range between approximately 60 and 120 ° on. As a result, sufficient heat dissipation from the hot angular segment region H is ensured, with supercooling of the cold angular segment region C being avoided.
    9 shows a central housing part 2a with a cooling channel arrangement 53 consisting of axial cooling channels 53a. Holes 42a for fastening screws 42 are arranged between cooling channels 53a. As is apparent, in particular, from the detailed illustration of the central cooling channel arrangement 53 shown in FIG. 14, a wet-running fastening screw is provided at the point designated 42b. The fastening screw penetrates the corresponding cooling channel 53a and is surrounded by coolant directly. This space can be saved and optimal heat dissipation at the place of ignition initiation, especially in the area around and / or between spark plugs, guaranteed.
    Fig. 10 shows a lateral second housing part 2c. In the region of the end face 36 facing the piston 4, the second housing part 2c has a cooling channel arrangement 54 consisting of a single kidney-shaped or arcuate cooling channel 54a, the cooling channel 54a extending from the cold angular segment region C to the hot angular segment region H over an angular range γ around the axis 10a of the eccentric shaft 10 extends from about 250 °. The coolant outlet from the second side coolant channel arrangement 54 is indicated by reference numeral 58. - 9 -
    It can be seen from FIGS. 8 and 10 that the first housing part 2b and the second housing part 2c have completely differently shaped piston-side cooling channel arrangements 52, 54. The piston-side cooling channel arrangements 52 and 54 differ both in the number of cooling channels and in the angular ranges α, β, γ over which the cooling channels 52a, 54a extend. This design allows a uniform heat dissipation from the thermally stressed areas of the power generation unit 40, wherein each component of the power unit 40 can be heated to the optimum operating temperature.
    FIGS. 11 to 16 each show coolant channel arrangements 51, 52, 53, 54 of the housing 2.
    In Fig. 11 and 12, the Kühlmittekanalanordnungen 51 and 52 are shown in the second housing part 2b. According to the arrow S, the coolant passes via the inlet 57 into the electro-side cooling channel arrangement 51. A first coolant stream flows according to the arrows Si from the beginning of the loop-like cooling channel 51c of the electro-side cooling channel arrangement 51 via two flow passages 60a, 60b directly into the first zone arranged in the hot angular segment region H. Cooling chamber 52a of the first piston-side cooling chamber arrangement 52 and passes via axial cooling channels 53a of the central cooling channel assembly 53 to the cooling chamber 54a of the second piston-side cooling channel assembly 54. A second coolant stream S2 flows to the end of the loop-like cooling channel 51c along the circumference of the jacket region 2b 'and from there via the Flow passage 60c in the arranged in the cold angle segment region C second cooling chamber 52b of the first piston-side cooling chamber assembly 52. From the second cooling chamber 52b, the second coolant stream S2 flows through the axial cooling channels 53a of the central n cooling channel arrangement 53 into the cooling space 54a of the second piston-side cooling space arrangement 54, where a mixing with the first coolant flow Si takes place. The common coolant flow S leaves the second piston-side cooling channel arrangement 54 via the outlet 58.
    In order to achieve excessive cooling of the hot angular segment region H and optimum temperature control of the various components, approximately 70% to 90%, for example 84%, of the total volume flow in the first coolant flow and 10 to 30%, for example 16%, are transported in the second coolant flow , A rough division takes place through the two flow passages 60a, 60b of the first coolant flow and the flow passage 60c of the second coolant flow from the loop-like cooling channel 51c into the first and second cooling chambers 52a, 52b. Fine tuning may be accomplished by defining accurately the flow crossings 61 disposed in the first or second side plates 8, 9 from the arcuate first cooling channel 52a into the axial cooling channels 53a of the central cooling channel assembly 53 by throttling the inlet, and by forming the central cooling channel assembly 53 in the central one Housing part 2a done.
    13 and 14 show front views of the cooling chambers 52a, 52b and 54 of the first and second piston-side cooling channel arrangement 52, 54. To avoid, for example cavitation damage in the transition region between the first and second housing part 2b, 2c and side plate 8, 9 has it has proven to be advantageous if at least one cooling channel 52a, 52b, 54a of the first or second piston-side cooling channel arrangement 52, 54 in at least one inner arc portion 52 ', 54' has a crescent-shaped channel portion 52a ', 54a' with stepped channel cross-section. In the crescent-shaped channel part 52a ', 54a', the flow cross-section is reduced. In order to sufficiently cool the area between the fastening screws, in the outer arc regions 52 ", 54 " the cooling channels 52a, 52b, 54a nicheartige bulges 52a ", 52b", 54a " intended.
    权利要求:
    Claims (19)
    [1]
    1 56088v2p. * ·. ^ kten ^: 2B A. i9}. ^ 2010 I: I Klp3 $ e. · ·, · · ·, · F · OJ. C (*) * (new) PATENT CLAIMS * t. 1. Rotary piston internal combustion engine (1) with at least one in a chamber: (3) of a housing (2) circulating rotary piston (4), wherein the chamber (3) of a trochoidenförmigen running surface (5) in a central Gehäuseteil§ (2a) and spaced from each other, normal to an eccentric shaft (10). * • * arranged lateral running surfaces (6, 7) is formed, wherein on both sides of »+ the central housing part (2a) in the direction of the axis (10a) of the eccentric shaft (10) directly or indirectly lateral housing parts (2b, 2c) connect, wherein at least one cooling channel arrangement (52, 53, 54) in the lateral first housing part (2b), in the central housing part (2a) and in the lateral second housing part (2c) of the piston internal combustion engine (1) of cooling liquid of a cooling circuit (50a) of a cooling system ( 50), wherein a first piston side cooling channel arrangement (52) of the lateral first housing part (2b), a central cooling channel arrangement (53) of the central housing part (2a) and a second piston side cooling channel arrangement (54) of the lateral second housing part (2c) in the cooling circuit (50a) of the cooling system (50) are successively flowed through in the order given, characterized in that at least one cooling channel (52a, 52b, 54a) of he The second or the second piston-side cooling channel arrangement (52, 54) has a channel part (52a ', 54a') with reduced channel cross-section in at least one inner arc region (52 ', 54'). 2. rotary piston internal combustion engine (1) according to claim 1, characterized in that in the region of the first housing part (2b) or a first housing part (2b) final lid part (2d) a coolant inlet and in the region of the second housing part (2c) or a second Housing part (2c) final cover part (2f) a coolant outlet is arranged. 3. rotary piston internal combustion engine (1) according to claim 1 or 2, characterized in that in the region of a first side tread (6) forming the first side wall (8a) arranged first piston-side cooling channel arrangement (52) at least one in a hot READY 2 • · ··· * 1 - - * angular segment range (H) of the rotary piston internal force jTl ^ c & iri ^ Cä.iSteh.'üm- an angle (a) of at least 180 ° kidney- or arcuately extending first cooling channel (52a), which with the central cooling channel arrangement (53) is fluidly connected. * 4. The rotary piston internal combustion engine (1) according to claim 3, characterized in that the first piston-side cooling chamber arrangement (52) separated from the first cooling channel (52a), with the central cooling channel assembly (53) flow-connected kidney or • arcuate second cooling channel (52b ) in a cold angular segment region (C) of the rotary piston internal combustion engine (1), wherein the second cooling chamber (52b) over an angular range (ß) between 60 ° to 120 °, preferably 90 ° about the axis (10a) of the eccentric shaft (10 ). 5. rotary piston internal combustion engine (1) according to one of claims 1 to 4, characterized in that the second housing part (2c) in the region of the second guide surface (7) forming the second side wall (9a) with the central cooling chamber arrangement (53) flow-connected second piston side Wherein the second piston-side cooling chamber arrangement (54) has a kidney- or arcuate cooling channel (54a) arranged in the hot angular segment region (H) of the rotary piston internal combustion engine (1), which extends over an angular range (γ) of at least 180 °, preferably of at least 225 °, more preferably by an angular range of at least 240 °, about the axis (10a) of the eccentric shaft (10). 6. rotary piston internal combustion engine (1) according to one of claims 3 to 5, characterized in that the first and the second piston-side cooling chamber arrangement (52, 54) have different numbers of cooling chambers (52a, 52b, 54a) and / or the cooling chambers (52a, 52b, 54a) of the first refrigerator compartment assembly (52) and the second refrigerator compartment assembly (54) cover different angular ranges (α, β, γ) about the axis (10a) of the eccentric shaft (10). 7. A rotary piston internal combustion engine (1) according to any one of claims 1 to 6, characterized in that the first and / or the second side wall POSSIBLE (8a, 9a) by a between the lateral first bz i /; 2f) and the central housing part (2a) arranged separate side plate (8, 9) is formed, which preferably made of different * * * material * than the lateral first and second housing part (2b, 2c) or the central Housing part (2a) consists. ; 8. The rotary piston internal combustion engine (1) according to one of claims 1 to 7, characterized in that the lateral first housing part (2b), the I central housing part (2a) and the second housing part (2c), preferably ** at least one side plate (8, 9), by axially parallel fastening screws (42) are interconnected, wherein at least one in the hot angular segment region (H) arranged fastening screw (42) is made wet and an axis-parallel cooling channel (53 a) the central cooling channel arrangement (53) penetrates. 9. rotary piston internal combustion engine (1) according to one of claims 1 to 8, characterized in that the channel part (52a ', 54a') is sickle-shaped. 10. rotary piston internal combustion engine (1) according to one of claims 1 to 9, characterized in that the channel part (52 a ', 54 a') has a stepped cross-section. A rotary piston internal combustion engine (1) according to any one of claims 1 to 10, characterized in that at least one cooling passage (52a, 52b, 54a) of the first or second piston side cooling passage arrangement (52, 54) is formed in at least one outer arc section (52 ", 54 " ) has at least one niche-like bulge (52a ", 52b ", 54a "). 12. A rotary piston internal combustion engine (1) according to any one of claims 1 to 11, characterized in that each piston-side cooling channel arrangement (52, 54) via preferably in the side plates (8, 9) arranged flow cross-sections (61) with a defined flow cross section with preferably one axial cooling channel (53a) is fluidly connected to the central cooling channel arrangement (53), wherein at least one flow transition (61) has a smaller flow cross section than the corresponding axial cooling channel (53a). POSSIBLE 4 13. A rotary piston internal combustion engine (1) according to any one of the claims!]; bte: i2, i: characterized in that coaxially with the eccentric shaft (10) at least one electric machine (14) in the same housing (2) is arranged and rotary piston internal combustion engine (1) and electric machine (14) a power generator (40), in particular for the range expansion of an electric vehicle, forming a unit ^ · 'preferably wherein the rotor (13) of the electric machine (14) with the. ♦ ·, eccentric shaft (10) of the rotary piston internal combustion engine (1) rotatably connected * «is connected. 14. The rotary piston internal combustion engine (1) according to claim 13, characterized in that for cooling the electric machine (14) in the lateral first housing part (2b) an electro-side cooling channel arrangement (51) is arranged, which in the cooling circuit (50a) of the cooling system ( 50), wherein preferably the cooling channel arrangements (51, 52, 53, 54) of the electrical machine (14) receiving lateral first housing part (2b), the central housing part (2a) and the lateral second housing part (2c) in the cooling circuit ( 50a) are successively flowed through bar. 15. Rotary piston internal combustion engine (1) according to claim 13 or 14, characterized in that the electro-side cooling channel arrangement (51) in the inlet region of at least one electric machine (14) surrounding the cylindrical jacket portion (2b ') of the first housing part (2b) at least one loop-shaped annular channel (51c), wherein the first cooling passage (52a) and the second cooling passage (52b) of the first piston-side refrigerator assembly (52) are fluidly connected to different portions of the annular passage (51c). 16, rotary piston internal combustion engine (1) according to claim 14 or 15, characterized in that the electro-side cooling channel arrangement (51) and the first piston-side cooling channel arrangement (52) at least partially in parallel in the cooling circuit (50 a) of the cooling system (50) are arranged.
    [2]
    2. Rotary piston internal combustion engine (1) according to claim 1, characterized in that in the region of the first housing part (2b) or the first housing part (2b) final lid tare (2d) a coolant inlet and in the region of the second housing part (2c) or a second Housing part (2c) final cover part (2f) a coolant outlet is arranged.
    [3]
    3. rotary piston internal combustion engine (1) according to claim 1 or 2, characterized in that in the region of a first side tread (6) forming the first side wall (8a) arranged first piston-side cooling channel arrangement (52) at least one in a hot angular segment range (H) the rotary piston internal combustion engine (1) by an angle (a) of at least 180 ° kidney or arcuately extending first cooling channel (52a) which is fluidly connected to the central cooling channel arrangement (53).
    [4]
    4. rotary piston internal combustion engine (1) according to claim 3, characterized in that the first piston-side cooling chamber arrangement (52) separated from the first cooling channel (52 a), with the central cooling channel arrangement (53) flow-connected kidney or arcuate second cooling channel (52 b) in a cold Angular segment region (C) of the circular - 12 - has engine (1), wherein preferably the second cooling chamber (52b) over an angular range (ß) between 60 ° to 120 °, particularly preferably of 90 ° about the axis (10a) Exzenterwelie (10) extends.
    [5]
    5. rotary piston internal combustion engine (1) according to one of claims 1 to 4, characterized in that the second housing part (2c) in the region of the second guide surface (7) forming the second side wall (9a) with the central cooling chamber arrangement (53) flow-connected second piston side Refrigerator arrangement (54), wherein preferably the second piston side cooling chamber arrangement (54) one, more preferably only a single in the hot angular segment region (H) of the rotary piston internal combustion engine (1) arranged kidney or arcuate cooling channel (54a) softens over an angular range ( γ) of at least 180 °, preferably of at least 225 °, particularly preferably by an angular range of at least 240 °, about the axis (10a) of the eccentric wave (10).
    [6]
    6. rotary piston internal combustion engine (1) according to one of claims 3 to 5, characterized in that the first and the second piston side cooling chamber arrangement (52, 54) are different, preferably different numbers of cooling chambers (52 a, 52 b, 54 a) and / or have Cooling chambers (52a, 52b, 54a) of the first cooling chamber arrangement (52) and the second cooling chamber arrangement (54) cover different angular regions (α, β, γ) about the axis (10a) of the eccentric shaft (10).
    [7]
    7. rotary piston internal combustion engine (1) according to one of claims 1 to 5, characterized in that the first and / or the second side wall (8a, 9a) by a between the first side and second housing part (2b, 2c) and the central housing part (2a) arranged separate side plate (8, 9) is formed, which preferably consists of different material than the lateral first and second housing part (2b, 2c) or the central housing part (2a).
    [8]
    8. rotary piston internal combustion engine (1) according to one of claims 1 to 6, characterized in that the lateral first housing part (2b), the central housing part (2a) and the second housing part (2c), preferably also at least one side plate (8, 9) , are connected to one another by axially parallel fastening screws (42), wherein at least one fixing screw (42) arranged in the hot angular segment region (H) is wet and penetrates an axially parallel cooling channel (53a) of the central cooling channel arrangement (53). - 13 -
    [9]
    9. rotary piston internal combustion engine (1) according to one of claims 1 to 8, da-; characterized in that at least one cooling channel (52a, 52b, 54a) of the first or second piston-side cooling channel arrangement (52, 54) has a preferably crescent-shaped channel part (52a ', 54a') in at least one inner arc region (52 ', 54'). having a reduced, preferably stepped, channel cross-section. * •
    [10]
    10. rotary piston internal combustion engine (1) according to one of claims 1 to 9, da-; characterized in that at least one cooling channel (52a, 52b, 54a) of the first or second piston-side cooling channel arrangement (52, 54) has at least one niche-like recess (52a "f 52b", 54a ") in at least one outer arc portion (52", 54 "). ) having.
    [11]
    11, rotary piston internal combustion engine (1) according to one of claims 1 to 10, characterized in that each piston-side cooling channel arrangement (52, 54) via preferably in the side plates (8, 9) arranged flow cross-sections (58) with a defined flow cross-section with preferably each axial cooling channel (53a) is fluidly connected to the central cooling channel arrangement (53), wherein at least one flow transition (61) has a smaller flow cross section than the corresponding axial cooling channel (53a).
    1. A piston-type internal combustion engine (1) having at least one rotary piston (4) circulating in a chamber (3) of a housing (2), the chamber (3) being guided by a trochoidal running surface (5) in a central housing part (2a). and of spaced-apart, perpendicular to an eccentric shaft (10) arranged lateral running surfaces (6, 7) is formed, wherein on both sides of the central housing part (2a) in the direction of the axis (10a) of the eccentric shaft (10) directly or indirectly lateral housing parts ( 2b, 2c), wherein at least one cooling channel arrangement (52, 53, 54) in the lateral first housing part (2b), in the central housing part (2a) and in the lateral second housing part (2c) of the piston internal combustion engine (1) of cooling liquid of a cooling circuit (50a ) of a cooling system (50), characterized in that a first piston-side cooling channel arrangement (52) of the lateral first housing part (2b), a central cooling channel arrangement (53) of the central housing part (2a) and a second piston-side cooling channel arrangement (54) of the lateral second housing part (2c) in the cooling circuit (50a) of the cooling system (50) are successively flowed through in the order given.
    [12]
    12. rotary piston internal combustion engine (1) according to one of claims 1 to 1, characterized in that achsgieich with the Exzenterweile (10) at least one electric machine (14) in the same housing (2) is arranged and rotary piston internal combustion engine (1) and electric machine (14) a unit forming a power generator (40), in particular for the range expansion of an electric vehicle, wherein preferably the rotor (13) of the electric machine (14) with the eccentric shaft (10) of the rotary piston internal combustion engine (1) is rotatably connected,
    [13]
    13. Rotary piston internal combustion engine (1) according to claim 12, characterized in that for cooling the electric machine (14) preferably in the lateral first housing part (2b) an electro-side cooling channel arrangement (51) is arranged, which in the cooling circuit (50 a) of the cooling system (50). wherein, preferably, the cooling channel arrangements (51, 52, 53, 54) of the electrical machine (14) receiving lateral first housing part (2b), the central housing part (2a) and the lateral second housing part (2c) in the cooling circuit (50a) can be flowed through in succession. - 14 - - 14 - «. t
    [14]
    14, rotary piston internal combustion engine (1) according to claim 12 or 13, characterized in that the electro-side cooling channel arrangement (51) in the entry area at least one of the electrical machine (14) surrounding cylindrical shell region (2b ') of the first housing part (2b) at least one preferably More preferably, the first cooling channel (52a) and the second cooling channel (52b) of the first piston-side cooling chamber arrangement (52) are flow-connected to different areas of the annular channel (51c).
    [15]
    15. rotary piston internal combustion engine (1) according to claim 13 or 14, characterized in that the electro-side cooling channel arrangement (51) and the first piston-side cooling channel arrangement (52) at least partially in parallel in the cooling circuit (50 a) of the cooling system (50) are arranged, preferably a through the second coolant flow supplied to the loop-shaped annular channel (51c) and particularly preferably second cooling channel (52b) is smaller than a first coolant flow fed directly to the first piston-side cooling channel arrangement (52), preferably to the first cooling channel (52a).
    [16]
    16, rotary piston internal combustion engine (1) according to claim 15, characterized in that the first coolant flow after passing through cooling channels (52a, 53a) in the hot angular segment area (H) with the second coolant flow after the passage of cooling channels (52b, 53a) in the cold angular segment area (C) in the region of the second koibensei-term cooling channel arrangement (54) of the second housing part (2c) combined.
    [17]
    17. A rotary piston internal combustion engine (1) according to claim 16, characterized in that a through the loop-shaped annular channel (51c) and then supplied to the second cooling channel (52b) supplied FOLLOW 5 second coolant flow is less than a directly erstön tCdlbertSeitJcJeri: cooling channel arrangement (52) , the first coolant flow supplied to the first cooling passage (52a).
    17. rotary piston internal combustion engine (1) according to claim 15 or 16, characterized in that the volume flow of the first coolant flow about 70% to 90%, preferably 80 to 88%, of, preferably the housing (2) supplied and / or from the second piston side Cooling passage arrangement (54) of the second lateral housing part (2c) discharged total coolant flow is. 2010 11 18 Fu / St

    T # l! < * 4i 1) WS «9 33-Ö fa« (* 411) 892 89 333





    REPLACED 51



    REPLACED 2

    SUBSEQUENT



    ΘΟ

    SUBSEQUENT
    [18]
    18.Circular piston internal combustion engine (1) according to claim 16 or 17, characterized in that the first coolant flow after flowing through cooling channels (52a, 53a) in the hot angular segment range (H) with the second coolant flow after the passage of cooling channels (52b, 53a) in cold angle segment region (C) in the region of the second piston-side cooling channel arrangement (54) of the second housing part (2c) united.
    [19]
    19.Kreiskolbenbrennkraftmaschine (1) according to one of claims 16 to 18, characterized in that the volume flow of the first coolant flow about 70% to 90%, preferably 80 to 88%, of the housing (2) supplied and / or from the second piston side Cooling passage arrangement (54) of the second lateral housing part (2c) discharged total coolant flow is.

    2011 09 29 Fu / St r.j · -f ··. ! '·; ·; '- l. * " &Quot; r / ': a: *' ...... · ··. ·· * FOLLOWING
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    同族专利:
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    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    US3007460A|1960-03-29|1961-11-07|Curtiss Wright Corp|Cooling arrangement for rotary mechanisms|
    US3280802A|1963-10-26|1966-10-25|Nsu Motorenwerke Ag|Fluid cooled housing wall for internal combustion engines|
    DE2519907C2|1975-05-03|1977-06-02|Juergen Dipl-Ing Lambrecht|ROTARY LISTON MACHINE IN TROCHOID DESIGN|
    DE3545821C2|1985-12-23|1989-06-01|Wankel Gmbh, 1000 Berlin, De|
    DE3601193A1|1986-01-17|1987-07-23|Zeise Elektromaschinenbau Gmbh|Unit consisting of electric generator and internal combustion engine for boats|
    DE4020416C2|1990-06-27|1992-11-19|Metallwarenfabrik Gemmingen Gmbh & Co, 7519 Gemmingen, De|
    DE10124561A1|2000-05-27|2001-11-29|Brandenburgische Forschungs Un|Rotary piston engine with rotor and side plates uses plate of sealing disk and two cast parts and wall round combustion space ribbed on non-combustion side so tensile ribs radiate at right angle spacing onto bearing flange.|
    DE102008026920A1|2007-12-01|2009-06-04|Michael Dr. Fabritius|Rotary piston combustion engine, has end side part designed as two-parts, where end side part comprises end-side path part that is bent toward piston, and end-side covering part that is bent away from piston|
    DE102008015031B4|2008-03-17|2014-10-23|Wankel Super Tec Gmbh|Housing for a rotary engine and rotary engine|
    AT505950B1|2009-02-05|2010-04-15|Avl List Gmbh|POWER GENERATION UNIT|DE102012215018A1|2012-08-23|2014-02-27|Robert Bosch Gmbh|Housing for an electric machine with a meandering cooling channel and guide geometries|
    JP2020114046A|2019-01-08|2020-07-27|株式会社デンソー|Rotary electric machine|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    ATA1912/2010A|AT510749B1|2010-11-18|2010-11-18|LOBE internal combustion engine|ATA1912/2010A| AT510749B1|2010-11-18|2010-11-18|LOBE internal combustion engine|
    PCT/EP2011/070341| WO2012066072A2|2010-11-18|2011-11-17|Rotary piston internal combustion engine|
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