CN1146230A - Reciprocating machine - Google Patents
Reciprocating machine Download PDFInfo
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- CN1146230A CN1146230A CN 95192665 CN95192665A CN1146230A CN 1146230 A CN1146230 A CN 1146230A CN 95192665 CN95192665 CN 95192665 CN 95192665 A CN95192665 A CN 95192665A CN 1146230 A CN1146230 A CN 1146230A
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- machine
- crankshaft
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Abstract
A reciprocating machine comprising a working piston and cylinder assembly, a counter rotating crank drive having an inner crankshaft carrying an eccentric in driving connection with the piston, the eccentric being rotatable within a big end bearing housing and the piston being connected to said bearing housing, wherein the inner crank shaft is eccentrically journalled about an intermediate axis in a single outer crankshaft which is rotatably mounted relative to a crank case of the machine for rotation about a main axis, the inner crank shaft having an inner gear in engagement with an outer ring gear stationary with respect to the crank case.
Description
The present invention relates to reciprocator, comprise a working piston and cylinder assembly, one has the counter-rotating crank driving part of an inside crankshaft, inside crankshaft supporting one eccentric wheel that is connected with piston actuated, and eccentric wheel can rotate in a big-end bearing case and piston is connected on the described bearing housing.
This machine is internal-combustion engine or an external-combustion engine or a compressor for example.
GB-B-2080483 discloses the reciprocator of the above-mentioned type, wherein eccentric wheel is connected on the relative axle journal that is arranged on the eccentric wheel opposite side by alternate connecting plate, thereby inside crank is adorned axle journal prejudicially in two outer crankshafts axially aligning and be rotatably mounted with respect to crankcase.Inside crankshaft have one link to each other with each axle journal and with a corresponding stationary gear meshed gears.
The shortcoming of this machine is not only to need to make the rotation axis of two outer crankshafts that separate accurately to align, and must accurately circumferentially align mutually with the engagement between the gear that the axle journal of single bent axle links to each other.It is difficult making the alignment of this wide relatively part that separates reach desired validity in practice.In addition, it is more expensive relatively to make this machine, and this is not only because need to obtain this kind alignment, and because needs many parts.In addition, machine is relatively large along the overall dimensions of the rotation axis direction of paired outer crankshaft.
In addition, this machine vibrates owing to unbalanced force and cyclical disequilibrium when having single or being easy to during piston that number is less.
An object of the present invention is to provide a kind of this machine, can overcome or reduce above-mentioned shortcoming.Another object of the present invention provides a kind of this machine, wherein can overcome or reduce above-mentioned additional shortcoming.
According to the present invention, a kind of such reciprocator is provided, wherein inside crankshaft is adorned axle journal in a single outer crankshaft that is rotatably mounted with respect to the crankcase of machine prejudicially around a medial axis, to rotate around main axis, inside crankshaft has the internal gear with the outer tooth ring engagement static with respect to crankcase.
Interior external gear is respectively equipped with outer interior commutating tooth or spiral or helical teeth.
Outer crankshaft can by on vertically apart the position that is arranged on bent axle and two bearings that are preferably disposed on the opposite side of described external gear its axle journal is connected in the crankcase.
Outer crankshaft can be provided with the bearing means that is provided with along on the alternate position on its length direction, and wherein the alternate axle journal of inside crankshaft is rotatably installed on wherein.
The described alternate axle journal of inside crankshaft can be arranged on the opposite side of described external gear.
Can be provided with an otch that holds internal gear on the outer crankshaft.
Eccentric wheel can become cantilever to install by inside crankshaft.
Can be provided with another axle journal on the inside crankshaft, at eccentric opposite side facing to bearing, thereby inside crankshaft is installed in rotation on the outer crankshaft, and described another axle journal can be with respect to a countershaft eccentric rotary, and the rotation axis that countershaft is mounted to around outer crankshaft rotates with respect to crankcase.
This machine also can have another working piston and cylinder assembly, and this another piston is connected on the big-end bearing case that another described eccentric wheel can rotate therein.
Perhaps, when inside crankshaft is provided with described another axle journal that can rotate with respect to described countershaft, this machine can have one second working piston and cylinder assembly, this second piston is connected on the second largest step bearing case that one second eccentric wheel can rotate therein, second eccentric wheel is connected in second journal rest in one second countershaft to axle journal prejudicially by one, it is rotatably mounted with respect to crankcase by another second axle journal, wherein, other axle journal is all with respect to the eccentric rotation of described countershaft, and each other axle journal for example radially is oppositely arranged with predetermined angular dependence.
If for example, need a pto in the end of the machine that is provided with another axle journal; Or need one second and put piston and cylinder assembly; Or for example for the power input of twice is provided, with two of shaft orientation relation installations or the piston that has cantilevered eccentric wheel separately in groups; Or in order to connect two machines with difference in functionality, for example a motor and a compressor then can be provided with this other axle journal.
Be provided with under the situation of another axle journal at all these, need provide and the corresponding second pair of gear of this other axle journal.
Especially when machine has the piston of or lesser amt, it is easy to owing to unbalanced force and periodic uneven the vibration, therefore, in order to overcome this additional problem, one inner equilibrium Weight apparatus can be set so that the quality that small part ground dynamical balancing is rotated around medial axis is provided with an outer counterweight device so that the quality that small part ground dynamical balancing is rotated around main axis.
The internal and external equilibrium Weight apparatus preferably is set, and each center of gravity is coaxial with medial axis and main axis respectively as a result for it.
Therefore, inside crankshaft has an inner equilibrium Weight apparatus, and outer crankshaft has an outer counterweight device, and the center of gravity of outer counterweight device is radially relative with the formed center of gravity of counterweight device with inside crankshaft.
The inner equilibrium Weight apparatus comprises the first and second inner equilibrium Weight apparatus that are arranged on each side of piston center line, thereby avoids or reduce any moment around the piston center line.
The inner equilibrium Weight apparatus comprise a single inner equilibrium Weight apparatus or a plurality of vertically alternate inner equilibrium Weight apparatus.
Described a plurality of inner equilibrium Weight apparatus is included on the opposite side of piston the vertically first and second alternate counterweight devices.
Single or at least one inner equilibrium Weight apparatus comprises a plurality of radially alternate counterweights.
Outer counterweight device comprises a single outer counterweight device or an a plurality of vertically alternate outer counterweight device.
Described a plurality of outer counterweight device is included in the locational first and second vertical alternate outer counterweight devices of outer crankshaft.
Single or at least one outer counterweight device can comprise a plurality of radially alternate counterweights.
Outer counterweight device can comprise one first and one second outer counterweight device, respectively has a center of gravity, is arranged on the vertical alternate position of outer crankshaft and is arranged on its radially opposite side.
The counterweight that comprises single or multiple outer counterweight devices is arranged on the outer crankshaft any desired location or along on the lengthwise position of its rotation axis, and/or be located on the auxiliary element that separates with outer crankshaft and be arranged to therewith rotate auxiliary drive shaft for example.
A drive unit be installed and be provided with to auxiliary element can be driven with the rotating speed identical with it by outer crankshaft by bearing means.
When machine has a countershaft, can the establishing thereon to small part of outer counterweight device.
Outer counterweight device can comprise first and second vertical alternate outer counterweight devices, and first vertical alternate outer counterweight device is located on the described outer crankshaft, and second vertical alternate outer counterweight device is located on the described countershaft.
The embodiment of reciprocator of the present invention is described below with reference to the accompanying drawings.In the accompanying drawing:
Fig. 1 passes the schematic cross section that embodies internal-combustion engine of the present invention;
Fig. 1 a is the partial section that is shown in further detail the internal-combustion engine of Fig. 1;
Fig. 2 is the part schematic end view of machine shown in Figure 1;
Fig. 3 is the partial cross sectional view of the second embodiment of the present invention;
Fig. 4 is the partial cross sectional view of the third embodiment of the present invention;
Fig. 5 is the schematic cross section that the 4th embodiment of narrow V-2 structure internal-combustion engine is shown;
Fig. 6 is the part schematic end view of machine shown in Figure 5;
Fig. 7 is the schematic cross section of fifth embodiment of the invention, and the motor of two-phase countercylinder structure is shown;
Fig. 8 is the more detailed schematic cross section of motor shown in Figure 7;
Fig. 9 is the schematic cross section of another embodiment of the present invention;
Figure 10 illustrates the schematic cross section that embodies another internal-combustion engine of the present invention;
Figure 10 a illustrates in greater detail motor shown in Figure 10;
Figure 11 is another embodiment's of the present invention schematic cross section;
Figure 12 is another embodiment's of the present invention schematic cross section;
Figure 12 a illustrates in greater detail motor shown in Figure 12;
Figure 13 is another embodiment's of the present invention schematic cross section; And
Figure 14 is the schematic transverse cross-sectional view of motor shown in Figure 13.
Identical label is represented identical parts in institute's drawings attached.
Referring to Fig. 1,1a and 2, the motor shown in the figure comprises a working piston and cylinder assembly, this assembly comprise one in the cylinder 12 that is provided with cylinder buss 14 pistons reciprocating 10.In common mode one firing chamber 16 is set.
A piston 10 and a bar 17 are rigidly connected, and are connected to a big-end bearing case 18 by this bar, and the while and one is bearing in one and can be connected around 20 drivings of the eccentric wheel on the inside crankshaft 22 that medial axis Y-Y rotates.Piston 10 can be connected with bar 17 by one " small end " if desired, but this is unnecessary.
The inside crankshaft 22 supportings first and second inner equilibrium Weight apparatus of vertically being separated by, each Weight apparatus comprises an inner equilibrium piece 24, it is arranged to directly vertically adjacent with eccentric wheel and is positioned at eccentric opposite side with counterbalanced eccentric, piston support and frame set 20,10,17 and 18 weight, thus the center of gravity of the quality of rotating around axis Y-Y is overlapped with axis Y-Y.
The axle journal of inside crankshaft 22 is contained on the outer crankshaft 26 prejudicially to rotate around axis Y-Y.Outer crankshaft 26 itself is installed in rotation in the crankcase 28 to rotate around a main axis X-X by main bearing 30,32.
In the running, inside crankshaft 22 rotates around the direction of the direction of rotation of its axis X-X with outer crankshaft 26 around its axis Y-Y edge.External gear 54 is 2: 1 with the gear ratio of ring gear 56, thereby inside crankshaft 22 is its twice with respect to the sense of rotation of outer crankshaft 26 and outer crankshaft 26 with respect to the direction of rotation and the rotating speed of crankcase.The geometrical center of eccentric wheel 20, shown in Y-Y among the figure, along the straight reciprocating motion shown in the A, thereby piston 10 is along the accurately to-and-fro motion of its axis.
Because structure and operation that the counter-rotating crank drives are well-known, are not described in detail in this.This driving can be by the following interior anti-counterweight device that will describe 24 and the dynamical balancing fully of outer counterweight device.
Referring to Fig. 1, outer crankshaft 26 is provided with the flywheel that a supporting comprises the outer counterweight device of one first outer counterweight device 58.
Yet, because the cantilever design of counterweight device 58 is with respect to the weight axialy offset of wanting balance and for fear of unbalanced moment takes place, make pouring weight 58 greater than the required weight of dynamical balancing radially, and bearing 30 vertically with first outside counterweight device 58 radially be oppositely arranged counterweight device 60 outside one second.The size of the first and second counterweight devices 58,60 is arranged to be compensated by pouring weight 60 by the moment that the eccentric position of pouring weight 58 produces, and pouring weight 58,60 guarantees that together the center of gravity of the quality of rotating around axis X-X is consistent with axis.
If desired, can be along pouring weight 60 and/or pouring weight 58 are set in any position of outer crankshaft 26.In addition, in the outer counterweight device 58 and 60 one or both can be arranged to an independent pouring weight or at a plurality of pouring weights with respect to different amount and/or the lengthwise position of axis X-X, thereby make the General of each pouring weight part equal required weight and position.
For example, another of pouring weight 58 shown in Fig. 1 a or additional position 58 '.
In another embodiment, as shown in Figure 3, it is the part by an air cooling single cylinder diesel, this diesel engine has a long relatively flywheel 57, just along the long flywheel of X-X axle direction, the first counterweight device 58 can be contained on the inner face of flywheel, as 58 " shown in, replace or be attached to the weight of establishing on the relevant position of the first counterweight device 58 ' among Fig. 1 a.Certainly, if weight be located among Fig. 1 a 58 ' and be located at 58 " the position, two weight summations equal the quality of requirement.
In another embodiment, as shown in Figure 4, flywheel 57 is formed by the rotor of brushless generator, and the first counterweight device can directly be fixed on the rotation seat C of the permanent magnet (top illustrates different magnet structures with the bottom among Fig. 4) that supports brushless generator, among Fig. 4 shown in 58 .Pouring weight 58 can append to or replace pouring weight 58 as shown in Figure 4.
In another example, shown in Fig. 3 and 4 70, motor has one to camshaft and/or oil pump or be positioned at the actuator with respect to another auxiliary member of the opposite end of normal clutch end of motor, auxiliary member or axle 70 are provided with a pouring weight 58a, and it can make the quality of rotating around axis X-X obtain dynamical balancing as its part with at least one the pouring weight that is arranged on aforementioned other position described in previous examples.
But the weight of counterweight block 60 is defined as the balance longitudinal moment and radially is oppositely arranged with counterweight block 58, and the weight of pouring weight 58 is increased to an amount greater than the required weight that equals pouring weight 60 of machine radial equilibrium.
By piston 10, the adverse effect of the weight Mosc of connecting rod 17 and crank pin axle journal 20 and the weight Mb of pouring weight 24 can obtain correct balance, is crank pin radius " R " (22 and 26 throw of eccentric) thereby need the real radius of the parts of balance.The real radius of pouring weight 24 needn't be " R ", and can be any length " L ", as long as this length satisfies:
M
osc*R＝M
b*L
The axial position of inner equilibrium Weight apparatus 24 preferably equals M
OscFor this reason, pouring weight 24 preferably separates and is arranged on the both sides of connecting rod.But inside crankshaft counterweight device 24 and oscillating mass addition and concentrate on its rotation axis Y-Y like this, and thereby can be by above-mentioned outer counterweight device balance.
The quality of counterweight block is meant the effective mass at each center of gravity radius of gyration in this manual.
Although have only a piston in this example, if desired, motor can be provided with the piston more than.Any crank pin that is positioned on the pitch diameter of gear 54 will carry out straight-line oscillation in all directions.Be installed in any piston on this crank or the pin can be by the reaction of 24 pairs of total oscillating mass of inner equilibrium Weight apparatus with suitable quality and position balance.Perhaps, connecting rod 17 can extend along the footpath of connecting rod shown in the figure 17 and link to each other with another piston assembly round about.Certainly, all suitable cylinder can be set in all cases.
Fig. 5 and 6 illustrates the another embodiment of the present invention of narrow V-2 type cylinder structure.
This motor is with shown in Figure 1 different, and it is provided with the composite eccentric wheel assembly that has at a distance of the eccentric wheel 20 of certain angular distance, as shown in Figure 6, and have one with second piston and the corresponding second largest step bearing case 18 of cylinder assembly.
Fig. 7 illustrates another example with two opposed cylinders, and one of them single big end housing body 18 has and two-piston 10 rigidly connected piston rods 17.Moreover certainly, piston can be connected on the bar 17 by one " small end " bearing.
Should notice that in this embodiment the first outer counterweight device 58 is bearing in the inner of outer crankshaft 26, and the second outer counterweight device 60 is by flywheel 57 supportings.
Fig. 8 illustrates and illustrates in greater detail the motor shown in Fig. 7.
In this embodiment, all rotary bearings of motor can be the bearing of roll piece type.Especially, in this embodiment, the bearing between the interior outer crankshaft is a rolling bearing 41 ', 42 ', and they are corresponding to the sliding bearing 41,42 shown in Fig. 1 a and 2, thereby eccentric wheel 20 becomes cantilever to install by the remaining part of inside crankshaft 22.
If desired, can on the opposite side of this piston or each piston, be provided for the additional support of inside crankshaft 22, for example, if that end at motor needs power output, perhaps one second piston arranged side by side if desired, motor with counter-rotating crank driving device is set so that the power output of twice to be provided if perhaps be in line along axis, perhaps, for example the machine (for example a motor and a compressor) with two kinds of difference in functionalitys couples together.
Fig. 9,10,10a illustrates two examples of the machine with this additional support that is used for inside crankshaft.
In these situations any, do not need to provide in second pair and external gear, thereby avoid the difficulty of above-mentioned acquisition angular alignment.
Only needing on the axle of described opposite end can provide supporting around orbit rotation around the rotational of outer crankshaft and at the countershaft of the described opposite end of motor another axle journal of eccentric support by one.
Fig. 9 illustrates four-stroke two cylinder arranged side by side, and wherein eccentric wheel 20 axially extends and is contained in rotationally in the second largest step bearing housing of second piston 10.Also be provided with an axle journal 51 at this end eccentric wheel 20, it is rotatable and be installed in prejudicially can be in the countershaft 53 that axis X-X rotates, and axle journal 51 can rotate around axis Y-Y.
Figure 10 and 10a illustrate another example of the present invention, and the remodeling of the present invention with piston arranged side by side and cylinder assembly is shown.
Shown in right side among Figure 10 and the 10a, one of piston 10 described in above-mentioned embodiment, drive be connected to one with eccentric wheel 20 that inside crankshaft 22 links to each other on, but provide in addition one can be with respect to the axle journal 109 of countershaft 105 eccentric rotary.Yet, it should be noted that outer crankshaft 26 is provided with a gear 120, it and another gear 120a engagement are to output power to a for example camshaft charger or a generator.
The big-end bearing case 18 of another piston 10 in left side is received on one second eccentric wheel 20 rotationally in Figure 10 and 10a, this eccentric wheel by one by the bearing 113 in second countershaft 115,114 second axle journals 112 rotatable and that install prejudicially support, second countershaft 115 is installed in rotation in the crankcase 28 by bearing 116,117.Second axle journal 112 is not provided with a gear corresponding to gear 54.
Therefore, igniting and the inertial load from each inside crank supported the countershaft 105 that these supportings are common, and countershaft and axle journal 109,110 joints by relatively large bearing 103,104.Because torque load, the drive end of inside crankshaft is provided with a little block bearing, shown among the figure 41.
Figure 11 illustrates another example of the present invention, wherein needs to provide a generator and charger apparatus.In this case, if at couple positioned opposite one countershaft of piston, flywheel 57 preferably is installed in the sidepiece of motor, and motor is provided with the high load of pitch wheel 54,56 to avoid producing owing to torque ripple on the intermediate bearing 41,42.
In order to utilize the space best, flywheel 57 preferably should be a jar shape, as shown in Figure 11 and other accompanying drawing.Therefore, flywheel is generally columniform wall 57a and can comprises permanent toroidal magnet 130 with any required number of poles.It is interior to form holistic brushless generator that stationary armature 131 can be installed in ring, and this generator can match with the full power output of motor.Because the electric energy that produced is proportional and oversize for fear of the flywheel flux loop with the peripheral velocity of magnet ring, a planet retarder can be set to increase the rotating speed that encircles between engine output shaft and flux loop.This embodiment is as shown in Figure 12 and 12a.
Be provided with one and comprise a sun gear 81, the planetary reducer 80 of a planetary pinion 82 and a ring gear 83 to be increasing the output speed of motor, and is used to cover a brushless generator 85 that is arranged on the drum 86 that is locked on the axle of sun gear 81 around the space of a tubulose bearing extension part 84.
Flywheel as shown in Figure 12 and 12a can support another gear device and drive an at a high speed paired charger with the needs that adapt to the running of two strokes.
Referring now to Figure 13 and 14,, there is shown two stroke opposed cylinder structures of a band charging piston.
As mentioned above, relative piston 10 is connected on the eccentric wheel 20 by an inside crankshaft 22 supportings drivingly.Inside crankshaft 22 also has another eccentric wheel 140, it rotate with eccentric wheel 20 that rotation axis Y-Y has identical radius but with its at a distance of certain angle offset, and be connected to by another bearing housing 141 on the piston rod 143 of the piston 144 that in cylinder body 145, slidably charges.One end of cylinder body 145 is provided with a suction valve 146 and an outlet valve 147, and has a suction valve 148 and an outlet valve 149 at the other end.Outlet valve 147 is connected to the inside of the cylinder body 12 that links to each other with one of piston 10 by a suction valve 151 by one first pressure chamber 150, and outlet valve 149 is connected to the inside of the cylinder body 12 that links to each other with another piston 10 by one second suction valve 153 by one second pressure chamber 152.Therefore, the to-and-fro motion along with the to-and-fro motion of piston 10 of charging piston is with charging that working cylinder 12 is hocketed.Motor also is provided with common oil trap 154 and is used for the outlet valve 155 of cylinder 12.
Pressure chamber 150,152nd is set, and in order to look after 90 ° of phase angles between charging piston and the working piston, but when high engine speed, these can not need.
Although between interior outer crankshaft, sliding bearing is set in the above-described embodiments, if desired, can rolling bearing is set between them.
Although above-mentioned example is an internal-combustion engine, the present invention and above-mentioned and here shown in structure characteristic can be applicable to other reciprocator, for example external-combustion engine or compressor or pump.
In all embodiments, although only show a pair of intermeshing in external gear 54,56, if desired, can apart many to external gear in intermeshing are set axially, they can rotate around the single inside crankshaft on axial side of piston 22.This a pair of or describedly manyly provide a single intermeshing internal-external gear arrangement to gear.
If desired, machine can comprise a plurality of embodiments reciprocator of the present invention.
Above disclosed feature, or following claims, or accompanying drawing, with their specific forms or finish the term or the mode of required function, or the method that is used to obtain disclosed result can this feature be used for realizing in a different manner the present invention individually or in combination.
Claims (30)
1. reciprocator, comprise a working piston and cylinder assembly, one has the counter-rotating crank driving part of an inside crankshaft, the eccentric wheel that crankshaft support one is connected with piston actuated, eccentric wheel can rotate in a big-end bearing case and piston is connected on the described step bearing case, wherein inside crankshaft is connected in axle journal in the one single outer crankshaft that is rotatably mounted with respect to the crankcase of machine prejudicially around a medial axis, to rotate around main axis, inside crankshaft has the internal gear with the outer tooth ring engagement static with respect to crankcase.
2. according to the machine of claim 1, it is characterized in that interior external gear is respectively equipped with outer interior commutating tooth or spiral or helical teeth.
3. according to the machine of claim 1 or 2, it is characterized in that outer crankshaft is connected in its axle journal in the crankcase by vertical locational two bearings apart that are arranged on bent axle.
4. according to the machine of claim 3, it is characterized in that described bearing is arranged on the opposite side of described external gear.
5. according to the machine of above-mentioned each claim, it is characterized in that outer crankshaft is provided with the bearing means that is provided with along on the alternate position on its length direction, the alternate axle journal of inside crankshaft is rotatably installed on wherein.
6 machines according to claim 5 is characterized in that, the described alternate axle journal of inside crankshaft is arranged on the opposite side of described external gear.
7. according to the machine of above-mentioned each claim, it is characterized in that outer crankshaft is provided with an otch that holds internal gear.
8. according to the machine of above-mentioned each claim, it is characterized in that eccentric wheel becomes cantilever to install by inside crankshaft.
9. according to the machine of above-mentioned each claim, it is characterized in that, also be provided with another axle journal on the inside crankshaft, at eccentric opposite side facing to bearing, thereby inside crankshaft is installed in rotation on the outer crankshaft, described another axle journal can be with respect to a countershaft eccentric rotary, and the rotation axis that countershaft is mounted to around outer crankshaft rotates with respect to crankcase.
10. according to the machine of above-mentioned each claim, it is characterized in that this machine also has another working piston and cylinder assembly, this another piston is connected on the big-end bearing case that another described eccentric wheel can rotate therein.
11. machine according to claim 9, it is characterized in that, this machine has one second working piston and cylinder assembly, this second piston is connected on the second largest step bearing case that one second eccentric wheel can rotate therein, second eccentric wheel is connected in second journal rest in one second countershaft to axle journal prejudicially by one, it is rotatably mounted with respect to crankcase by another second axle journal, wherein, other axle journal is all with respect to the eccentric rotation of described countershaft, and each other axle journal is with predetermined angular dependence setting.
12. machine according to above-mentioned each claim, it is characterized in that, one inner equilibrium Weight apparatus is set so that the quality that small part ground dynamical balancing is rotated around medial axis is provided with an outer counterweight device so that the quality that small part ground dynamical balancing is rotated around main axis.
13. the machine according to claim 12 is characterized in that, the internal and external equilibrium Weight apparatus is set, each center of gravity is coaxial with medial axis and main axis respectively as a result for it.
14. the machine according to claim 13 is characterized in that, inside crankshaft has an inner equilibrium Weight apparatus, and outer crankshaft has an outer counterweight device, and the center of gravity of outer counterweight device is radially relative with the formed center of gravity of counterweight device with inside crankshaft.
15., it is characterized in that the inner equilibrium Weight apparatus comprises the first and second inner equilibrium Weight apparatus that are arranged on each side of piston center line according to each machine in the claim 12 to 14.
16., it is characterized in that the inner equilibrium Weight apparatus comprises a single inner equilibrium Weight apparatus according to each machine in the claim 12 to 15.
17., it is characterized in that the inner equilibrium Weight apparatus comprises a plurality of vertically alternate inner equilibrium Weight apparatus according to each machine in the claim 12 to 15.
18. the machine according to claim 17 is characterized in that, described a plurality of inner equilibrium Weight apparatus are included on the opposite side of piston the vertically first and second alternate counterweight devices.
19., it is characterized in that single or at least one inner equilibrium Weight apparatus comprises a plurality of radially alternate counterweights according to each machine in the claim 16 to 18.
20., it is characterized in that outer counterweight device comprises a single outer counterweight device according to each machine in the claim 12 to 19.
21., it is characterized in that outer counterweight device comprises a plurality of vertically alternate outer counterweight devices according to each machine in the claim 12 to 19.
22. the machine according to claim 21 is characterized in that, described a plurality of outer counterweight devices are included in the locational first and second vertical alternate outer counterweight devices of outer crankshaft.
23., it is characterized in that single or at least one outer counterweight device comprises a plurality of radially alternate counterweights according to each machine in the claim 20 to 22.
24. the machine according to claim 21 is characterized in that, outer counterweight device comprises one first and one second outer counterweight device, respectively has a center of gravity, is arranged on the vertical alternate position of outer crankshaft and is arranged on its radially opposite side.
25. according to each machine in the claim 12 to 24, it is characterized in that, the counterweight that comprises single or multiple outer counterweight devices is arranged on the outer crankshaft any desired location or along on the lengthwise position of its rotation axis, and/or is located on the auxiliary element that separates with outer crankshaft and is arranged to therewith rotate.
26. the machine according to claim 25 is characterized in that, auxiliary element is installed and is provided with a drive unit to be driven with the rotating speed identical with it by outer crankshaft by bearing means.
27., it is characterized in that being located on the described countershaft to small part of outer counterweight device according to each machine in the claim 12 to 25 that is subordinated among the claim 9-11 each.
28. machine according to claim 27, it is characterized in that, outer counterweight device comprises first and second vertical alternate outer counterweight devices, and first vertical alternate outer counterweight device is located on the described outer crankshaft, and second vertical alternate outer counterweight device is located on the described countershaft.
29. as mentioned above and referring to accompanying drawing 1 to 2; Fig. 3; Fig. 4; Fig. 5 and 6; Fig. 7 and 8; Fig. 9; Figure 10 and 10a; Figure 11; Figure 12 and 12a; Or the reciprocator shown in Figure 13 and 14.
30. describe here and any new feature of the novel combination of feature shown in the drawings.
Applications Claiming Priority (5)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| GB9407966A GB9407966D0 (en) | 1994-04-21 | 1994-04-21 | Cantilevered crankshafts |
| GB9407966.2 | 1994-04-21 | ||
| GB9420891A GB9420891D0 (en) | 1994-10-17 | 1994-10-17 | Cantilevered crankshafts |
| GB9420891.5 | 1994-10-17 | ||
| GB9501948.5 | 1995-02-01 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN1146230A true CN1146230A (en) | 1997-03-26 |
Family
ID=26304751
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 95192665 Pending CN1146230A (en) | 1994-04-21 | 1995-04-19 | Reciprocating machine |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN1146230A (en) |
-
1995
- 1995-04-19 CN CN 95192665 patent/CN1146230A/en active Pending
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