Patent Grant
11174859
This application is the U.S. national phase of PCT Application No. PCT/DE2014/100352 filed on Oct. 8, 2014, which claims priority to DE Patent Application No. 10 2013 111 098.3 filed on Oct. 8, 2013, the disclosures of which are incorporated in their entirety by reference herein.
The present invention relates to a turbomachine which can be operated both as a hydraulic motor and as a pump, with a shaft which is mounted in an axially fixed fashion, comprising a power section and a controller which comprises at least one connecting part on which at least one distributor part with through-openings and at least one feed part, are arranged, wherein the distributor part is driven by means of at least one drive which is arranged on the shaft, and axial forces are distributed to a piston which is arranged axially on the distributor part, wherein the at least one inflow and outflow provided on the machine section is configured in a rotating fashion and is supplied by the distributor part and the piston, via the feed part, with at least two driving pressures which rotate concomitantly, wherein the driving pressures, with their annular faces, projected in association therewith, on the piston generate forces. In the text which follows, a power section is to be understood as being a machine which is supplied, for operation, with at least two feed pressures which rotate concomitantly, and for this purpose has an output which drives the distributor part of the turbomachine. The machine here may be either an adjustable or a non-adjustable machine.
A hydrostatic rotary piston engine with a non-variable volume flow is already known from the prior art in WO 2006/010471 A1. Furthermore, EP 0166995B1 describes a hydrostatic rotary piston machine with an infinitely variable volume. These machines can be operated either as a motor or as a pump and function with both right-hand rotation and left-hand rotation, and accordingly each have two operating modes as motor and pump in both senses of rotation and consequently four quadrants (motor with right-hand rotation, motor with left-hand rotation, pump with left-hand rotation and pump with right-hand rotation).
The disadvantage here is that very high pressure-dependent and rotational-direction-dependent axial forces occur in these machines. These forces give rise to very high pressure-dependent and rotational-direction-dependent friction losses. As a result, these machines are non-linear, have different properties during right-hand rotation and left-hand rotation and have reduced efficiency.
Further disadvantages of these solutions which are already known are described below. The unequal and non-linear behavior of the machines during right-hand rotation and left-hand rotation in both modes make them entirely unsuitable for many applications such as, for example, for use as wheel hub motor or, for example, for use as a measuring system or servo drive. A wheel hub motor, for example, must have precisely the same properties during right-hand rotation and left-hand rotation so that the left and right wheels are driven equally. The reduced efficiency also makes the machines unattractive for various applications and at the same time generates a lot of waste heat, which is even completely unacceptable in many applications. The unequal behavior during right-hand rotation and left-hand rotation is due to the design and can therefore be influenced only within quite narrow limits, by changing geometric parameters, during the configuration. Under certain pressure conditions it may even be found that such machines enter a state in which a very strong internal short-circuit flow arises and the function of the machine in one sense of rotation, and at least one operating mode, is even no longer provided; therefore, the entire function is not reliably ensured. In order to start up, the machines require very high pressure differences, which often prevents the possibility of use of such a drive. Moreover, machines of this design function only according to the three-tube principle with an inflow, outflow and separate leakage outflow. Further disadvantages of these machines are that they do not have a free-wheeling function, braking function or a soft start and also have no blocking function. In addition, the characteristic of the machines cannot be adapted to changed conditions during operation in all four quadrants. Furthermore, these machines are suitable only for operation with fluids owing to the large minimum pressure differences.
DE 10 2008 025 054 B4 discloses a hydraulic unit for making available a pressurized hydraulic fluid for driving a hydraulic actuator which is coupled thereto and which is equipped with a motor which is arranged in a pressurized motor housing, a hydraulic accumulator which is arranged in an accumulator housing, as well as a hydraulic pump arranged in a pump housing and a hydraulic block. It is characteristic of said hydraulic units that at least the motor housing, pump housing and the hydraulic block form a standardized rigid module which is easy to handle, and the hydraulic fluid flowing around in the module passes through all the elements of the module in the longitudinal direction (circulation system) in certain areas. The significant element of this hydraulic unit is that the hydraulic pump and the hydraulic block form one functional unit, the hydraulic block is provided with a multiplicity of hydraulic connection elements, and by means of a flange a delivery chamber which is arranged in the pump housing is covered by the hydraulic block on the side facing the motor housing.
U.S. Pat. No. 3,853,435 A discloses a hydraulic device comprising a housing with a fluid feed opening and a fluid discharge opening, wherein a rotor in the housing and the stator are provided, and in addition a rotor which is rotatable with respect to the stator, and has a low-pressure zone and a high-pressure zone. A commutator valve is rotatably accommodated in the housing, wherein in two cavities a high-pressure zone and a low-pressure zone are connected to the fluid feed connection and the fluid output opening.
The present invention is based on the object of providing a turbomachine in which the axial forces are, with the exception of a minimum force for sealing the running faces, very low or even zero, and which turbomachine can be used both as a pump and a drive machine and can be operated with all conceivable fluids, wherein it is intended to operate equally with right-hand rotation and left-hand rotation, and the function is intended to be reliably ensured independently of the pressure configurations of the driving pressures.
According to the invention, the above object is achieved with the features of claim 1. Advantageous refinements of the turbomachine according to the invention are specified in the dependent claims.
Accordingly, a turbomachine of the type mentioned is characterized in that at at least one end side of the distributor part, at least one further pressure acts on at least one equivalent area, and the efficiency using the entire resulting force which presses together the contact faces between the piston and the distributor, as well as between the distributor and the feed part, is changed within an adjustment range.
The turbomachine is preferably to be capable of being implemented using the two-tube principle without a separate leakage outflow, and can be equipped with a control device and an associated drive, with the result that it maintains its high efficiency even at high pressures. The control device is to make it possible to implement a freewheeling function, a braking function, a blocking function, a soft start, linearization of the characteristic curves and adaptation of characteristic curves to specific load requirements within an adjustment range.
All of the forces acting on the distributor part are firstly in equilibrium in each of the four operating states of the turbomachine, both in the axial and radial directions, with the exception of a sealing force. In order to be able to keep the axial forces in equilibrium even independently of the rotational speed and sense of rotation, additional pressure regions are arranged on the distributor part in such a way that a regular pressure distribution, which is symmetrical in itself, is formed on the end side of the distributor part. This equilibrium can then be changed selectively by means of an additional control device which is preferably provided and which has a drive. A control device is to be understood in the text which follows as a force-transmitting means which transmits axial forces to the piston. This force is generated by a separate drive and can also be used for braking or soft starting or blocking or decoupling the turbomachine.
It was quite surprising for a person skilled in the art that with the turbomachine according to the invention all the abovementioned disadvantages no longer occurred. The significant and decisive advantage of the proposed turbomachine is that it is very functionally reliable in all four quadrants, has the same properties with right-hand rotation and left-hand rotation and achieves a significantly higher efficiency and very high starting torques by eliminating friction losses.
Further objectives, features, advantages and application possibilities of the turbomachine according to the invention can be found in the following description of an exemplary embodiment with reference to the drawings. Here, all the features which are described and/or illustrated figuratively form per se or in any desired combination the subject matter of the invention, independently of their combination in the individual claims or their back-reference.
In the drawings:
As is apparent from
The control device 13 acts on the piston 9 in the axial direction and is driven here by the drive of the control device 14. The two check valves 16, 17 are arranged between the inner leakage region 7 and the connections 5, 6.
A further pressure region 8, which is connected to the inner pressure region 7 via at least one feed line 24 in the feed part 11, is located at the outer edge of the distributor part 10.
A spring 15 generates a spring force Ff with which the piston 9 and the distributor part 10 are pressed onto the feed part 11, in order to seal these parts 10, 11 with respect to one another. Said spring 15 is arranged between the connection part 4 and the piston 9.
The axial and almost linear supply of the power section with the driving pressures p1, p2 is particularly advantageous here for the efficiency of the turbomachine 1. The flow of the fluid is hardly braked by deflections here.
In a further advantageous embodiment, the turbomachine 1 can also be embodied without a control device 13 with a drive of the control device 14. The advantage of this embodiment is that the turbomachine 1 becomes significantly more advantageous if none of the functions of freewheeling, soft start, braking or blocking are required in the application, but merely an advantageous machine with excellent efficiency and the same functionally reliable behavior with right-hand rotation end left-hand rotation.
As is apparent from
The characteristic curve K1 shows by way of example the behavior of a turbomachine 1 without a control device 13. K1 is already virtually symmetrical or even completely symmetrical in the four quadrants I-IV. The relatively high starting torque at the shaft Mw in the first two quadrants I, II during driving, and the high starting torque in the two quadrants III, IV during pumping are advantageous here. The starting is always reliably ensured even when there are very small pressure differences between the two driving pressures p1, p2. A small starting torque is important, for example, in windmills, which as a result do not start to generate energy at, for example 3 m/s wind speed but instead already at, for example, 1 m/s wind speed.
The characteristic curve K2 shows, for example, a characteristic curve of a turbomachine 1 with a control device 13 and the drive of the control device 14, in which characteristic curve K2 the efficiency is linearized in certain sections and has been optimized for high pressures within the adjustment range 19 in that the necessary sealing forces in the turbomachine 1 have already been adapted to the respectively present pressure conditions of the two driving pressures p1, p2 and to the rotational speed of the turbomachine 1.
The characteristic curve K3 shows by way of example a turbomachine 1 which behaves differently in the four quadrants I-IV within the adjustment range 19. The blocking of the machine is illustrated at point 20. At said point, nw=0 and Mw=0. The braking 21 is illustrated, for example, in the first quadrant I on the characteristic curve K3. In the second quadrant II, the adaptation 22 of the characteristic curve K3 is shown by way of example. The free-wheeling 23 is illustrated with right-hand rotation and left-hand rotation. At said point Mw=0 and nw≠0.
A further advantage is that the turbomachine 1 according to the invention can now be controlled. In conjunction with its improved properties, its more reliable functioning and the additional functions of free-wheeling, soft start, braking and blocking, it is suitable for a multiplicity of applications such as, for example, as locomotion drives, windmills, measuring systems, drives in safety-protocol applications or servo drives.
As is apparent from
If the turbomachine 1 is equipped with a control device 13 having a drive 14, the control force Fs also acts additionally. On the inside of the distributor part 10, different pressures act, and they are also not distributed constantly. The force Fgsx is calculated therefore generally as Fgsx=∫pA, nv dA. Depending on the embodiment, Fgsx is calculated as FgsA, FgSB or FgsC. The precise pressure ratios on this face are non-linear, rotational-speed-dependent and very complex.
A segment with, in each case, a through-opening 26 of the driving pressure p1 and a through-opening 27 of the driving pressure p2 is illustrated in an enlarged form in
In order to illustrate these complex pressure ratios more clearly, virtually constant gradient between two pressures p1, p2, pli, pw1, pw2 . . . is assumed below. This results in simplified equivalent areas A1, A2, A3 . . . , B1, B2, B3 . . . , C1, C2, C3 . . . , with which the pressures are then multiplied and can be multiplied to form FgsA, FgsB and FgsC.
The sum of all these forces Fp1, Fp2, Fs, Ff, Fl, Fw, Fgsx is the total resulting force Fgx which, depending on the embodiment, is designated as FgA, FgB, FgC. The turbomachine 1 cannot start until this total resulting force Fgx presses together the contact faces between piston 9 and distributor plate 10 and between distributor part 10 and feed part 11 to a sufficient, but not excessive, degree, and therefore seals them, without blocking. Otherwise, either the inner short-circuit flow Vki of the outer short-circuit flow Vka comes about, since the piston 9, distributor part 10 and feed part 11 are not sealed with respect to one another, or the turbomachine 1 even blocks, since the contact pressure that generates the Fgx between the piston 9, distributor part 10 and feed part 11, is too high. It is therefore particularly advantageous always to be able to set the force Fgx to an optimum degree to the operating point of the machine by means of the control device 13 and the associated drive 14.
A further advantage is that when the control device 13 with the drive 14 is present it is even possible to dispense with the spring 15 if the spring force Ff is generated by the driven control device 13, 14.
Furthermore, a further advantage is that according to the case in which the piston 9 and/or the distributor 10 and/or the control device 13 are of magnetic design, axial forces can also be generated in this way. A simple electromagnet can then be used, for example, as a drive for the control device 13.
As is apparent from
For the prior art, the action case A, where A1>>A2 is obtained. In the action case A, the total force FgsA is:
during left-hand rotation:
FgsA=p1*A1+p2*A2+pli*A3;
during right-hand rotation:
FgsA=p2*A1+p1*A2+pli*A3.
Both terms can only be equally large if A1=A2. However, this is precisely what never occurs here. Most of the serious disadvantages with conventional machines arise from this contradiction.
In action case B, a further pressure pw1 acts on the outside of the distributor part 10. The areas B1 and B2 are ideally equal in size. In the action case B, the total force FgsB on the end side of the distributor part 10 is:
During left-hand rotation:
FgsB=p1*B1+p2*B2+pw1*B3+pli*B4;
During right-hand rotation:
FgsB=p2*B1+p1*B2+pw1*B3+pli*B4.
Since the areas B1, B2 can be equal in size here, B1=B2. A total force at the end side FgB, and therefore also the force FgsB, are then equal in size irrespective of the sense of rotation.
It is advantageous that the turbomachine 1 now has gained the same or at least almost the same properties during right-hand rotation and left-hand rotation owing to the symmetrical conditions. A further advantage is that according to the case in which the further pressure pw1 is equal to the inner leakage pressure pi, the design of the turbomachine 1 is considerably simplified, since the pressure regions B3 and B4 now only have to be connected by feed lines 24.
In the action case C, the further pressure pw1 acts on the area C3 on the distributor part 10. The areas C1 and C2 are ideally equal in size. The area C4 is supplied with a further pressure pw2 via feed lines 24. This pressure may be, for example, the inner leakage pressure pli or else, as in the illustration, the further pressure pw1 which is present on the outside, or else also the control pressure pw2.
In the action case C, the total force FgsC at the end side of the distributor part 10 is therefore:
during left-hand rotation:
FgsC=p1*C1+p2*C2+pw1*C3+pw2*C4+pli*C5;
during right-hand rotation:
FgsC=p2*C1+p1*C2+pwl*C3+p2*C4+pli*C5.
Since the areas C1 and C2 can be equal in size here, C1=C2. The total force at the end side FgC and therefore also the total force FgsC can then be equal independently of the sense of rotation. If pli=pw1=pw2, the design of the turbomachine 1 is also in turn simplified considerably, since the pressure regions C3, C4, C5 only have to be connected by feed lines 24. This advantageously results in a multiplicity of conceivable configurations in order to optimize influence and optimize the properties of the turbomachine 1.
A further advantage is that a further pressure pw1 can also be fed in as a control pressure from the outside to the further pressure region 24 by means of at least one feed line, via the connecting part 4.
As is apparent from
It is advantageous that it now becomes possible to operate the turbomachine 1 with just two feed lines at all operating points only in conjunction with the same properties during right-hand rotation and left-hand rotation. The third leakage line for diverting the leakage flows Vla, Vli is dispensed with.
A further advantage is that the distributor part 10 is supplied axially via the piston 9 and the connecting part 4 virtually without deflection and the large cross-sections of the through-openings 26, 27 for the two driving pressures p1, p2 also result in very large flow cross-sections. Both of these things contribute to a high overall efficiency η.
A further advantage is also that the turbomachine 1 is optimized in terms of manufacture and technology in all of its parts, since, apart from a feed line to the further pressure region 24, there are no oblique boreholes.
As is apparent from
Since the shaft of the controller 2 is connected via the drive 12 of the distributor part 10 to the reduction ratio and to the distributor part 10, it is advantageously possible to brake by reversing the control force Fs of the distributor part 10 between the piston 9 and the feed part 11, and in this way directly influence the torque at the shaft Mw.
A further advantage is that the braking torque which arises when the free wheel is opened is very low, as no inner braking torques can arise anymore as a result of the total resulting force Fg.
As is apparent from
It is advantageous that pressure fluctuations of the driving forces p1, p2 in this embodiment no longer influence the total resulting force Fg. In this preferred embodiment, the control device 13 is advantageously composed of a fluid which is located in a cylinder which is arranged between the piston 9 and the two connecting parts 4. The drive of the control device 14 applies the control pressure to this fluid, and thereby generates the control force Fs. The distributor part 10 is driven by the drive 12 of the distributor part 10 with the rotational speed nv. In this context, the two check valves 16, 17 are arranged between the inner leakage region 7 and the connections 5, 6.
A further advantage of this embodiment of the turbomachine 1 is also due to the fact that the total system is operated by means of fluids thereby facilitating integration into a total system in which the control information is already present in the form of a control pressure.
As is apparent from
As is apparent from
The power section 2 with the rotating inflow and outflow is arranged on the feed part 11. The drive 12 of the distributor part 10 is arranged between the distributor part 10 and the power section 2. The power section 2 drives the distributor part 10 synchronously via the drive 12, with the result that both rotate the distributor part 10 synchronously with the rotational speed nv. Between the distributor part 10 and the power section 2 there is an adjustment angle ξ with the result that the pressure regions p1, p2 of the power section 2 can lead, be precisely in synchronism with or lag with respect to the distributor part 10. Depending on the design of the power section 2, a reduction ratio u for adapting the rotational speed is necessary for this.
It is advantageous here that the drive 12 of the distributor part 10 no longer has to be necessarily coaxial with the distributor part 10. A further advantage is that depending on the type of power section 2 the reduction ratio u can also be equal to 1, and therefore direct drive is possible, which does not give rise to any additional running noise. It is advantageous that the efficiency η and also the symmetry of the characteristic curves K0, K1, K2, K3 can be changed by means of the leading or lagging of the distributor part 10 with respect to the power section 2 by the adjustment angle ξ.
As is apparent from
In the first embodiment A, the power section 2 is composed of a GEROTOR machine with a constant volume flow, as can be seen in section in
In the second embodiment B, the power section 2 is composed of a GEROTOR machine with an adjustable volume flow. Said machine is illustrated in section. The most important advantage is the adjustability of the volume flow, which is absolutely necessary in many applications.
In the third embodiment C, the power section 2 is composed of an axial piston machine with a wobble plate. The shaft of this machine is connected directly to the distributor part 10 of the controller 3. The reduction ratio u is therefore equal to 1. This results in a particularly simple design, which can also be adjustable by means of the inclination of the wobble plate in the volume flow, and with u=1 permits a particularly simple and quiet direct drive of the controller 3.
In the fourth embodiment D, the power section 2 is composed of a radial piston machine with connecting rods and a crankshaft. The shaft of this machine is connected directly to the distributor part 10 of the controller 3. The reduction ratio u is therefore equal to 1.
A quite central advantage of the turbomachine 1 according to the invention is to combine it with a multiplicity of conceivable power sections 2 in order to provide an ideal solution for the respective application of the turbomachine 1.
| Number | Date | Country | Kind |
|---|---|---|---|
| 10 2013 111 098.3 | Oct 2013 | DE | national |
| Filing Document | Filing Date | Country | Kind |
|---|---|---|---|
| PCT/DE2014/100352 | 10/8/2014 | WO | 00 |
| Publishing Document | Publishing Date | Country | Kind |
|---|---|---|---|
| WO2015/051784 | 4/16/2015 | WO | A |
| Number | Name | Date | Kind |
|---|---|---|---|
| 3572983 | McDermott | Mar 1971 | A |
| 3799201 | Hansen | Mar 1974 | A |
| 3853435 | Ogasahara et al. | Dec 1974 | A |
| 4411607 | Wusthof | Oct 1983 | A |
| 4435130 | Ohrberg | Mar 1984 | A |
| 4635605 | Faupel et al. | Jan 1987 | A |
| 4992034 | Uppal | Feb 1991 | A |
| 7832996 | Eisenmann | Nov 2010 | B2 |
| 20080277239 | Gassmann | Nov 2008 | A1 |
| Number | Date | Country |
|---|---|---|
| 3015551 | Oct 1981 | DE |
| 3029997 | Feb 1982 | DE |
| 19520405 | Dec 1996 | DE |
| 102008025054 | Dec 2009 | DE |
| 0166995 | Jan 1986 | EP |
| 1074740 | Feb 2001 | EP |
| 2006010471 | Feb 2006 | WO |
| Entry |
|---|
| International Search Report for PCT/DE2014/100352, English Translation attached to original, Both completed by the European Patent Office on Mar. 30, 2015 Altogether 7 Pages. |
| Number | Date | Country | |
|---|---|---|---|
| 20160252083 A1 | Sep 2016 | US |
