DE2517666A1 - COMPENSATION DEVICE, IN PARTICULAR FOR DIRECT-ACTING MACHINES - Google Patents

Description

DIPL.-1NQ. JOACHIM STRASSE, HANAU DIPL-INQ. KLAUS QORQ, MUNICH

PATENT LAWYERS (8566)

HANAU RÖMERSTR. 19 POST BOX 793 TEL.r (06181) 20803/20740 TELEGRAMS: HANAUPATENT TELEX: 4184782 pat MUNICH 80 QRAFINQER STRASSE 31 TEL: (089) 405643 TELEX 522054 ostpa

Francois BERNARD

F-69OO3 Lyon (Rhone), France

Auguste MOIROUX ²² ' ^A *> ^{ril 1975}

Ecully (Rhone), France Gö / Jg - 11 236

Compensation device, in particular for direct acting machines

The invention relates to a compensation device, in particular for a direct acting machine with a reciprocating arrangement within a housing.

Free piston engines are known, the movable arrangement either by a symmetrical arrangement or is balanced by balancing weights, which are mechanically connected to the movable arrangement. Such Solutions are complicated and take up a lot of space.

The object of the present invention is to overcome these disadvantages by creating a compensating device avoid that does not require a mechanical connection with the movable assembly.

The invention solves the problem by means of at least one mechanical oscillator provided with an inertia block, which is attached to the housing of the direct-acting machine "in this way

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is that the direction of movement of the inertial block is parallel to the main axis of the movable assembly, the The characteristics of the oscillator are such that the external movements of the housing caused by the reaction of the moving arrangement is compensated by an opposite reaction of the same frequency, which is generated by the oscillator, so that a counter resonance is achieved.

The main advantage of the compensation device according to the invention is that the balance of the direct-acting machine is achieved without a mechanical Connection with the movable assembly is required. This will make the construction of the balancer much simpler and especially lighter. In addition, the dead weight of the movable assembly is not increased, which means that the movable assembly has a mass that corresponds to half the mass that required with a conventional balancing device were. It is known that for the same forces this increases the frequency and consequently that transmitted by the machine Power in the transmission

2m = 1-1 + 1

m
is.

According to another feature of the invention, the inertial block slides in a cylinder and is operated by feedback members returned to the center of the cylinder constant, each on the sides of the inertia block are arranged.

2517688 '

According to a modified embodiment of the invention the inertia block slides on a guide rod, constantly returning to the center, through return links, each arranged to the side of the inertia block are, with all parts in one housing. Material with a low coefficient of friction are arranged.

According to another feature of the invention, the return members are designed as spiral springs that are constantly are under tension.

According to a further feature of the invention, the return members have coil springs that are partially or are fully under tension, which increases their length.

According to another modified embodiment According to the invention, the compensating links are made of elastic material, for example neoprene, with the length of the links is chosen so that they are not subjected to any stress when the inertia block is in the center of the oscillator is located, and the shape of the members is such that the response generated thereby is linear is.

According to another modified embodiment According to the invention, the elastic members are formed by compressed gas, while the inertia block is a piston acts within the cylinder of the oscillating part. This piston can be aligned or provided with rings. The gas can e.g. B. Nitrogen mixed with lubricating oil be.

-U-

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According to another characteristic of the latter
A modified embodiment can be the inertia block
be brought back into the central position by two springs of low reaction, which are each arranged on the side of the inertia block.

According to another embodiment of the invention, the chambers filled with compressed air, each located on the side of the inertia block, can over
a conduit may be interconnected when the inertia block is in its central position, completely avoiding the use of mechanical springs.

According to another embodiment of the invention, additional spaces containing compressed gas are provided for the two chambers, these spaces being one
Allow linearization of the elastic response that
is generated by the two gas cushions. A pneumatically oscillating part has a response which is natural

pV ^ = K

follows, where K is a constant. This responsiveness is not linear. A linear response provides a much better stabilization of the oscillation conditions before. Then is the frequency of the oscillating part fixed and does not depend on the movement of the oscillating part.

According to another modified embodiment of the invention, the side gas cushions are with a
with compressed gas filled or fillable attached chamber connectable, the connection by a thermo

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static part is controlled in such a way that the temperatures of the two gas cushions are kept the same among each other. With this arrangement, an increase in the rigidity of the two gas cushions ″, which results from an increase, can be avoided the temperature of the gas cushions can result.

According to another feature of the latter, modified Embodiment, a detector is provided in addition to the thermostatic part on the machine, which reacts easily to the movement of the moving assembly of the direct acting machine and together with the thermostatic part controls the interaction between the side chambers and the additional chamber, so that the frequency of the oscillator is set as a function of the change in frequency of the direct-acting machine will. This feature is particularly important as it is an optimal alignment of the balancing device a function of the operating conditions (altitude, temperature and the like) and the state of the machine.

According to a last modified embodiment According to the invention, the piston-inertia block is centered by two low-reaction lateral springs is, an inner chamber, which is connectable to the side, gas-containing chambers, this connection can be produced by means of check valves, which flow the gas from the side chambers into the inner chamber let, while the inner chamber can be connected to the side chamber via a line during each stroke, in which the pressure is lowered when the piston inertia block reaches the corresponding dead center.

This latter line is primarily formed by bores that are arranged in the piston-inertia block,

-G-

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which on the one hand open into the inner chamber and on the other hand open into a central annular circumferential groove, which are provided in the outer wall of the piston. This rage stands in with elongated grooves in the inside wall of the cylinder Connection in which the piston slides.

Further details, features and advantages of the invention emerge from the following description of the FIGS accompanying drawings purely schematically illustrated embodiments. Show it:

1 shows a main view of a direct-acting machine or motor with a compensating device accordingly the invention,

Fig. 2 is a diagram showing the relative amplitudes - as a function of the relative Freq.uen-

F ^X 0
zen -

^F 0 '

3 shows a view of a mechanically oscillating part with compression springs,

FIG. K is a view of a modified embodiment, with the return springs being tensioned,

Fig. 5 is a view of the return elements, which consist of elastic material,

6 shows a view, the return elements being formed by air cushions and the inertia block being formed by centering springs in a central one Position is brought back,

Fig. 7 is a view corresponding to the centering of the inertia block takes place pneumatically,

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FIG. 8 is a diagram showing the mode of operation of the device according to FIG. 7,

9 shows a view of a pneumatically oscillating part with a linearizing device,

FIG. 10 is a diagram showing the mode of operation of the device according to FIG. 9,

11 is a view of a pneumatically oscillating part with a temperature correction,

FIG. 12 is a diagram showing the mode of operation of the device according to FIG. 11,

13 is a view of a pneumatically oscillating Partly with a rate adaptation "or adaptation,

FIG. 1h is a diagram showing the mode of operation of the device according to FIG. 13,

Fig. 15 is a view of another pneumatically oscillating one Partly with a frequency adaptation.

Fig. 1 shows a direct-acting machine which is provided with a compensating device Ui according to the invention. This direct-acting machine has a movable arrangement U2, which moves back and forth between a combustion chamber hk and an impact chamber U3. This latter chamber contains an air cushion which moves the movable arrangement k2 back in the direction of the combustion chamber UU.

The compensation device U1 is formed by an oscillating part, which consists of an inertia block 2, on which an oscillating movement is imposed. That

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The oscillating part is attached to the housing of the direct-acting machine in such a way that the direction of movement of the inertia block 2 is parallel to the main axis of the "movable assembly k2" .

The inertia block 2 slides within a cylinder 1. The block is constantly brought into a central position by two counteracting springs k6 and k "J, which are each arranged on one side of the inertia block 2. These springs are spiral springs and are constantly compressed in such a way that that they are live. The operation of the device is as follows:

When the direct acting machine is in operation, the movable assembly U2 is forced to move back and forth between the chambers ^ 3 and hk. As a result of this movement or the reaction forces, a reciprocating movement is correspondingly forced on a housing 50 of the direct-acting machine. Again, as a result of this action, a reciprocating motion is imposed on the inertial block 2 of the oscillating part. If the characteristics of the oscillating part or the compensating device k ^, in particular the natural frequency, are appropriately selected, the movement or the vibration of the housing can be eliminated. This corresponds to the point AR of the counter resonance (FIG. 2). This point coincides with the minimum of the dashed curve 51, which shows the relative

X '

ven movements - of the housing 50 represents. Among those

Conditions is the amplitude of the movement of the inertia block 2 at a maximum. The movement of the inertia block 2 is represented by a solid curve 52.

According to a modified embodiment of the invention the inertia block 2 slides on a guide rod

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(Fig. K ). In addition, the inertia block is returned to the central position by means of two oppositely acting spiral springs 56 and 57 which are under tension. This arrangement enables the frictional forces to be overcome to be reduced.

According to another modified embodiment According to the invention, the inertia block 2 is returned to the central position by two return members 58 and 59, which are made of elastic material such as "neoprene" "The length 60 of these return members is chosen in such a way that these links are not subject to any stress or stress in the central position of the inertia block 2. Are subject to deformation. -In addition, their shape is designed in such a way that the elastic reaction of these limbs is linearized.

According to another modified embodiment according to the invention, the inertial block 2 acts as a piston, and a gas under pressure is introduced into the chambers 5 and 6 through a check valve T. This valve is sealed by a shut-off element 8, which is welded after the filling process. Centering springs 3 and h are each provided on the side of the inertia block 2.

The operation of this latter modified embodiment is as follows:

With the pressurized gas, which is initially distributed over the chambers 5 and 6 as a result of the action of the springs 3 and h , the housing of the machine transmits the reciprocating motion to the inertial block 2. After a few strokes, the latter reaches its nominal

- 10 -

5 CS 3 A UI 0 4 3 3

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amplitude that stabilizes the housing 50.

According to a further modified embodiment of the invention, as shown in FIG. 7, openings 9 and 10 connect the elastic capacitors 5 and 6 to one another via a line 11 when the piston is located within the cylinder 1 in its central position. _f

The mode of operation of this last modified embodiment according to FIG. 7 takes place as follows:

If the gas masses in chambers 5 and 6 are different for any reason, the result is that the inertial block

2 is in a position shown by the point D in the diagram according to FIG. 8 at rest. The diagram shows the pressure in the chambers 5 and 6 as a function of the movement X of the inertia block 2. Among those Conditions, there is a gas transfer from one chamber to the other through line 11. Wake up a few strokes the centering of the inertia block 2 at the central point C.

According to a further embodiment according to the invention, a piston-inertia block 12 has inner chambers 61, 62, 63 and 6k, which are connected through transition openings 13 with annular grooves IU. A cylinder 15 , in which the piston inertia block 12 slides, is provided at each end with a connection opening or a connecting groove 16 which can be passed over or covered over by the piston 12.

The operation of this modified embodiment is as follows:

-11-

509844/0439

The chambers 61, 62, 63, 6h allow the reaction caused by the gas cushions 5 and 6 to be linearized so that the same frequency is achieved for the small and large movements and thus a faster coordination or a faster compensation of the oscillating conditions At the beginning the piston-inertia block 12 compresses the gas cushion in the chamber 5. Then after a certain movement to the left the piston connects the chamber 5 with the inner chamber 61 via the grooves 1U and the openings 13. Wach a further movement, the piston connects the chamber 5 and the inner chamber 61 with the inner chamber 62, etc. FIG. 10 shows the result of this subsequent movement.

From A to B the compression in the chamber 5, which has a large dead volume, is almost linear. From B to C is the Compression no longer linear, but thanks to the additional inner chamber 61, the pressure drops to C ', so that BC essentially is linear and so on. The chambers 61, 62, 63 and 6U can have an increasing volume, by as much as possible to achieve optimal linearity. Then, however, two series of additional inner chambers must be provided so that the gas cushions 5 and 6 work symmetrically. Of course, it is also possible to use these chambers instead of the Provide piston 12 in the cylinder.

According to a further modified embodiment of the invention comprises a piston inertia block I7 Inner chamber 18, which is provided with a central connection line 19. A cylinder 20 in which the Piston-inertia block 17 slides, has a central guide rod 21, which is arranged to slide and which on the one hand by a thermostatic material 22 and on the other hand, the one acting in the opposite direction

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Spring 23 absorbs forces. This rod 21 has an opening 2k at the edge, which connects the chamber 5 with the chamber 18 in the piston at the appropriate time via a line 25 arranged axially in the interior and a further opening 26 arranged at the periphery.

The operation of this modified embodiment is as follows:

With this device, the oscillation frequency is independent on the operating temperature in that when the temperature changes, the pressure cycle remains unchanged is held. This works for a reference temperature T thermostatis before material 22 on the rod 21 so that the Connection line 19 is located at point A of FIG. The diagram of FIG. 12 shows the average pressure of the Cycle as a function of the location of the connection line 19-Es it is found that at A is the average pressure of the cycle

corresponds to the boost pressure P. When the temperature of T ^ mo ^ ^ O

increases to T, P "is the average pressure in the 1 ml

Chamber 18 and chambers 5 and 6. The following applies

Formula: P ₁ = P ^T 0 ,, -, ν + ^ * τ *

ml mo τ = -. The print cycle then has the index

1
T instead of T. If the connection through openings 19 and 2k were to remain at the same point, then the pressure cycle would increase and the frequency would change. However, through the thermostatic means, the opening passes at point C, so that the chamber 5 is subjected to the pressure of the chamber at point C. Chamber 5 is thus uncharged in order to regain cycle P (T). A small approximation is achieved because the thermostatic correction is linear and the curve ρ = f (v) is exponential. The chamber 18 does not necessarily have to be in the piston, but, on the contrary, can be arranged in the cylinder housing 20. The volume of this chamber must be sufficient for the

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To supply chamber 5 correctly. A single device will only be required if the chamber 6 is automatic is supplied from the chamber 5 via a recentering line.

According to a further embodiment according to the invention (FIG. 13), a piston inertia block 27 has a line which is connected to the chamber 5 and which leads via line 29 to a circumferential groove 30. A cylinder 31 has an attached chamber 32, which is supplied from the chamber 5 via a check valve 33, which takes in air ύοώ the chamber 5 via a channel 3 ^ when the circumferential groove 30 faces an opening 35 which is connected to the channel 3 ^ is in connection and opens into the interior of the cylinder 31.

The operation of this modified embodiment is as follows:

In this modified embodiment, the frequency of the oscillating part can be regulated when the frequency of the machine changes. The mode of action results

from the representation in Fig. 1 ^. In this diagram

are the relative movements -rr of the housing 50 of the

^X 0

direct-acting machine (dashed curve) and the inertia block (solid curve). An operating point A chosen for the design lies below the counter resonance AR with a margin of safety. This point A corresponds to the maximum frequency of the machine, if it is in good condition and at sea level and is in line with the minimum temperature of the compressed gas in the oscillating part (e.g. -10 C). If the frequency of the machine is at the same temperature as the

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2517668

- Ik -

As the compressed gas drops _, point A tends to move toward point B and the oscillating part is detuned. The amplitude X drops in the process. In the same way, the point A tends to move towards the point B when the temperature of the oscillating part increases while the frequency of the machine remains constant. The oscillating part is detuned while its amplitude X. decreases. If both effects are combined with each other, the consequences also combine. The object of the proposed device is to keep the oscillating part in operation at point A by unloading the chamber 5 progressively into the storage chamber 32 until X is reached, the unloading process being stopped as soon as this point is reached. In this regard, the chamber 5 discharges through the check valve 33 into the storage chamber 32 as soon as the piston 27 compresses the gas in the chamber 5, starting from the abundant filling chamber already mentioned. The movement reaches optimal conditions, and the stroke increases from B to A. When the piston 27 reaches the piston stroke X., supplies the circumferential groove 30, which is supplied by the chamber 5 through the opening 28, the line and the circumferential groove 30, the opening 35, which directs the maximally compressed air of the chamber into the rear chamber of the valve 33. This latter chamber in the check valve, which was previously subjected to the main pressure of chamber 5, is immediately subjected to this new pressure and holds valve 33 in the closed position, whereby the discharge process is stopped. If the amplitude X. is not reached again, the chamber 36 discharges through a leak or through a calibrated or adjusted leak hole 37 , and the cycle begins again.

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509844/0439

This device also has the advantage that the chamber 5 is excessively charged during the first strokes takes place so that the rigidity is artificially increased. With increasing stroke, there is a discharge that increases compensated for the rigidity of the cycle. In this way it is essentially possible that before to avoid described linearization device. Of course, the chamber 6 is loaded via the recentering line. The loading chamber can either be outside the cylinder arranged in the piston as shown in FIG. 13 or as in a previously described example be ·

The device described above was essentially more harmonious and symmetrical to manufacture Oscillators directed with an accurate harmonic balance Move. It is possible in particular with the device described last, an asymmetrical Oscillator with a disharmonious movement too create, which is aimed at the compensation of different harmonies of the movement to be compensated. The movement of the oscillators then approaches the motion of the machine's motion assembly. In that regard, it is merely necessary, chambers 5 and 6 with different volumes and consequently relocate the position of the recentering line.

A final device according to the invention is shown in FIG shown. With this device, the frequency of the oscillator can be automatically adjusted when the frequency the machine changes or if the oscillator is out of tune.

This device consists of a cylinder TO, which receives a piston 71, which is actuated by two springs 72, 73

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5GS34WQ439

low rigidity is maintained. Chambers 7 ^ and 75 are of different sizes, while the bearing chamber "j6 is arranged within the piston 71. The chambers 7 ^ and 75 are sealed against one another by sealing rings 77. The bearing chamber 76 is supplied by the working chambers 7 ^ and 75 through check valves 78 The piston has a channel 79, which is supplied via openings 80. This cap establishes a connection between the bearing chamber 6 and the working chambers 71 and 75, specifically at specific times or positions of the piston through a groove 81.

This device works as follows:

At the beginning the elastic gas is about the three chambers 7 ^ + 5 75 and 76 distributed through internal leaks so that in the same pressure prevails in these chambers. As soon as the machine is started, the housing 50 moves and transmits they on the cylinder 70. The relative movements are on the mass 71 transmitted through the springs 72 and 73, the Movements of the piston 7I cause the compression of the Gas in the chamber 7 ^ · and 75 5 resulting in that gas high pressure from chambers 7 ^ - and 75 to storage chamber 76 flows; the excess of active gas decreases. The hub takes on a calculative and constructive basis Worth to. At this point the sealing rings open in the rage 81 and for a short time during which the stroke has reached its maximum, the gas can flow back from the storage chamber into the chambers 7 ^ and 75. Through this the balance between the inflow and outflow is ensured and the system works under permanent conditions Conditions. If any changes occur (change in the frequency of the machine or the frequency of the Oscillator), the system adapts itself to the stroke determined by the design.

Patent claims:

509344/0439

Claims (1)

- Π Patent claims: (1 .. Compensating device, in particular for a direct-acting machine, with an arrangement reciprocating inside a housing, geke η η ζ.e ichnet by at least one mechanical oscillator (Ui) provided with an inertia block (2), which is operated on the Housing (50) of the direct-acting machine is fixed in such a way that the direction of movement of the inertia block (2) is parallel to the main axis of the movable assembly (k2) , the characteristics of the oscillator [hl) being such that the external movements of the housing caused by the Reaction of the movable arrangement (U2) generated is compensated for by an opposite reaction of the same frequency, which is generated by the oscillator (U1), so that a counter resonance is achieved. 2. Compensation device according to claim 1, characterized characterized in that the inertia block (2) slides in a cylinder (1) and through return members for centering the cylinder is constantly returned, each arranged on the sides of the inertia block (2). 3. Compensation device according to one of claims 1 and / or 2, characterized in that that the inertia block (2) on a guide rod (55) constantly returning to the center slides, through return members, which are each arranged laterally of the inertia block (2), wherein all parts are arranged in a housing made of material with a low coefficient of friction. - 18 - 509844/0439 2517668 H. Compensating device according to at least one of Claims 1 to 3j, characterized in that the return members are spiral springs (k-6-, kj; 56 ", 57) which are constantly under tension. 5- compensation device according to at least one of claims 1 to 3, characterized in that the return elements have spiral springs which are partially or completely under tension stand, whereby their bulge length increases. 6. Compensating device according to at least one of claims 1 to 3s, characterized in that the compensating members (58, 59) are made of elastic material, for example neoprene, the length of the members is chosen so that they are not exposed to any stress when the inertia block (2) is in the center of the oscillator (h '\) , and the shape of the members (58, 59) is such that the response produced by them is linear. 7. Compensation device according to claims 1 and / or 2, characterized in that the elastic members are formed by compressed gas while the inertia block (2) acts as a piston within the cylinder (1). 8. Compensation device according to claim T, characterized characterized in that the inertia block is inserted into the central one by two low-reaction springs Position can be brought back, which are each arranged on the side of the inertia block (2). - 19 - 509844/0439 9. Compensation device according to claim 7, characterized in that the with compressed Gas-filled chambers (5, 6), which are arranged on both sides of the inertia block (2), via a line (11) are connected when the inertia block (2) is in the central position, wherein the inertia block (2) can be re-centered. 10. Compensation device according to at least one of the claims T to 9, characterized in that additional chambers (61, 62, 63, 6U) are provided so that the elastic reaction of the two gas cushions on both sides of the inertia block is linear, with each additional chamber subsequently connectable to the respective gas cushion (5 or 6) is when the gas of the corresponding chamber (5, 6) is compressed by the inertial block (2). 11. Compensation device according to at least one of the claims T-10, marked thereby ' net that the side gas cushions (5s 6) with a compressed gas filled resp. fillable attached chamber (18) are connectable, the connection through a thermostatic part (22) is controlled in such a way that the temperatures of the two gas cushions are kept the same with one another. 12. Compensation device according to at least one of the claims 1 to 11, characterized in that a detector is provided on the latter machine, which is easy on the movement the moving arrangement of the direct-acting machine reacts and the connection between the gas cushion - 20 - 509844/0439 and the attached chamber controls so that the frequency of the oscillator as a function of the frequency change the direct-acting machine is set. 13. Compensation device according to claims 7 and 8, characterized in that the piston-like inertia block ( ¹ Ji.), Which is re-centered by lateral springs with low reaction (72, 73), has an inner chamber (76) which is connected to the gas-containing lateral Chambers (7 ^ ₅ 75) can be connected via check valves (78), the check valves (78) allowing the gas to flow from the lateral chambers (7 ^, 75) into the inner chamber (76), while a line ( 81) connects the inner chamber (76) with the side chamber (7 ^ ·; 75) in which the pressure is lowered when the piston-like inertia block (71) reaches the corresponding dead center. 509844/0439 Blank page