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WO1979000652A1 - Machine de detente ou de compression de gaz ou de vapeurs - Google Patents

Machine de detente ou de compression de gaz ou de vapeurs Download PDF

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Publication number
WO1979000652A1
WO1979000652A1 PCT/SE1979/000037 SE7900037W WO7900652A1 WO 1979000652 A1 WO1979000652 A1 WO 1979000652A1 SE 7900037 W SE7900037 W SE 7900037W WO 7900652 A1 WO7900652 A1 WO 7900652A1
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WO
WIPO (PCT)
Prior art keywords
machine
working
space
reacting
rotation
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/SE1979/000037
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English (en)
Inventor
K Takalo
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Individual
Original Assignee
Individual
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Filing date
Publication date
Application filed by Individual filed Critical Individual
Priority to JP79500426A priority Critical patent/JPS56500222A/ja
Priority to BR7906804A priority patent/BR7906804A/pt
Publication of WO1979000652A1 publication Critical patent/WO1979000652A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C3/00—Rotary-piston machines or engines with non-parallel axes of movement of co-operating members
    • F01C3/02—Rotary-piston machines or engines with non-parallel axes of movement of co-operating members the axes being arranged at an angle of 90 degrees

Definitions

  • the present invention relates to a machine for expansion or compression of gases or vapours and to a use of the machine for storing and recovering energy.
  • the machine may also be used more generally as an engine or a compressor or in some other machinery involving volume alterations of gases or vapours.
  • the present invention also relates to perhaps the most important use of the invented machine, namely for storing electric or mechanical energy.
  • Machines performing expansion or compression of gases or vapours may be classified into turbo-machines and positive displacement machines.
  • Advantages associated with turbo-machines include great specific power, no need of power transmitting mechanisms, small wear and suitability for use of relatively cheap fuels in connection with a heat power process.
  • Disadvantages include losses of 10-20% in consequence of kinetic way of action, poor suitability for light gases as helium or hydrogen and a necessity to have the first part of a turbine at the maximum temperature of gas or steam in connection with a heat power process.
  • Typical drawbacks associated with known positive displacement machines include the need of power transmitting mechanisms, low specific power and disadvantages associated with sealing lubrication, namely power losses, temperature limitations as well as rapid wear.
  • types not using sealing lubrication are generally characterized by a great gas leak due to structures where sizes of leaking clearances depend on mutual synchronization between moving members, said synchronization being imperfect e.g. because of free play in gears.
  • the necessity of transmitting power through those mechanisms makes it further more difficult to avoid said play.
  • the lack of possibilities to reduce the speed of gas leak to a value lower than the velocity of sound is another main reason for great losses.
  • the present machine is characterized by small losses, no need of power transmitting mechanisms, in certain applications even a very great specific power, good suitability for light gases, small wear, no need of sealing lubrication and good suitability for high pressure levels as well as for various temperature levels.
  • the pressure level in a closed gas process the pressure level may be chosen freely, resulting in a great specific power even with a moderate volume flow, if the pressure level used is high enough.
  • a gas process has no limitations of steam as for temperature scale usable.
  • the waste heat of the process is released in a form usable for low or medium temperature purposes, as heating or water distillation, without any need for compromizing between electric efficiency.
  • the reason why a gas process is not widely used in this field lies in the fact that the only machine suitable for the process known heretofore has been a turbo-machine having so great losses that the efficiency of the gas process would remain essentially lower than that attainable with a Rankine cycle.
  • the invented machine were used as engines and compressors in a gas process using Brayton-cycle, provided with a heat exchanger between hot and cold sides, the efficiency attainable would be comparable with that of the steam process. Additionally, if the temperature range utilized were extended over that used in connection with a water steam process, an even considerably higher electric or mechanical efficiency than earlier could be achieved. Furthermore, the waste heat would be in a suitable form for various purposes. Heat energy used in a closed process may naturally be originated from any source. Thus, besides fuels also solar or nuclear energy might be utilized.
  • the invented machine might be very advantageous in solar energy applications, because it can be manufactured as a smaller unit than a turbine and still have a good efficiency as well as good specific power.
  • the weight of the machine per unit power is remarkably lower than that of a condensing turbine.
  • Brayton-cycle also a waste heat of the process is released in a useful form, all heat energy focus onto an absorbator by using mirrors could be utilized, partly as electricity, partly as heat.
  • heliostats reflecting radiation onto an absorbator there would be better changes than earlier to make profitably heliostats reflecting radiation onto an absorbator.
  • the invented machine with low losses may be valuable also in certain heat pump applications, e.g. for utilizing some low temperature waste heat or for air conditioning.
  • the invented machine fits particularly well to the purpose of storing energy, first of all due to minimum losses involved with the machine, and also due to good suitability for light working gases such as helium. Without the invented machine it would not be possible to carry out the storing process in a profitable form.
  • the storing process in accordance with the invention would be particularly advantageous in connection with use of solar, wind or wave energy.
  • the drawback associated with these alternative energy sources is a temporal variation of production. If the storing of energy is not arranged, the role of the alternatives mentioned is restricted to a partial saving of fuels, because then a full capacity of other types of power stations must exist.
  • the invented method may be regarded harmless due to very simple materials used.
  • the process is suitable also for. annual storing, which is an important aspect especially when solar energy is used. With the aid of the invention it is possible to base energy production even totally on solar energy. For supplying needs of vehicles the stored energy can be converted into some fuel, e.g. hydrogen. Even in this relation the invented process would be advantageous in eliminating the need for large hydrogen reserves, because a conversion into hydrogen may be done fairly well in time with consumption.
  • the invented machine is of positive displacement type having rotating moving parts. Expansion or compression is performed within the machine in periodically closing spaces, the volumes of which are varying periodically. No power transmitting mechanisms are necessary, but a torque caused by gas forces can effect directly a rotating working member and thus also a power shaft firmly connected to said member, the aspect mentioned being extremely important especially in the case of a high-power machine. Gas forces loading the rotor are symmetric in such a way that the only forces effecting the corresponding bearings are orginiated from the weight of the rotor, whence friction losses in the bearings remain unessential, particularly in connection with a closed process with a high pressure level.
  • the invented machine includes a body structure defining at least one rotation space therein, a working member rotatably mounted within said rotation space, one portion of the working member facing the surrounding body forming, together with the surrounding body, at least one working space moving with the working memeber circumferentially, and another portion of the working member being. provided with at least one separating wall extending close to the wall of the rotation space.
  • One functional basic unit of the machine includes n rotating reacting members equally distributed around the periphery of the rotation space in such a way that each reacting member is rotatable around its own axis, which is essentially perpendicular to the rotation axis of the working member and preferrably situated totally outside the rotation space of the working member.
  • the number of aforesaid working spaces situated one after another in circumferential direction is equal to the number of said reacting members or to an integral multiple thereof.
  • Each reacting member extends partially into the rotation space of the working member and has a part, which forms a transversal partition wall dividing the working space in question into two parts, a process space and a transferring space, respectively, the volumes of which vary periodically according to rotation of the working member.
  • Said partition wall forming part is shaped to have one, at the most two rotation sectors, called in the following transition sectors, in which the distance of the outer edge line to the rotation axis of the reacting member has a minimum value.
  • the machine also includes flow conduits in the body structure for the inlet and outlet of gas or vapour and at least one first opening in the body part surrounding the rotation space on the process space side of the partition wall for providing connection between the process space and the corresponding flow conduit, and at least one second opening positioned in the body structure on the transferring space side of the partition wall for providing connection between the trans ferring space and the corresponding flow conduit.
  • the machine further includes means for closing periodically the said first opening and synchronizing means interconnecting said working member, reacting members and closing means so that the connection between the process space and the corresponding flow conduit is established during such a part of the process cycle, during which the working space moves circumferentially over a certain distance, at one end of which the partition wall is in the process space end of the working space and that once for each process cycle a passage of one separating wall of the working member through one transition sector in the partition wall forming part of the reacting member is established.
  • the working member rotating around its middle axis may be firmly connected to a power shaft or they may be originally made of one single body.
  • an electric machine may directly load the working member, in which case the role of the shaft, if any, is only to support and position the working member.
  • Reacting members of one functional basic unit are situated at equal positions in the direction of the rotation axis of the working member and in the direction of the circumference thereof at intervals of an angle of 360o/n, in other words the whole circle divided by the number of reacting members.
  • n is a positive integer, one or greater.
  • the partition wall forming part of the reacting member is in practice a surface, which joins a fictive surface of revolution in realtion to the rotation axis of the reacting member.
  • a transition gap permitting a passage of the separating wall in the working member there through in connection with change of the process cycle is situated at a certain rotation sector of the partition wall forming surface.
  • Working spaces of one functional basic unit are situ ated one after another in the circumferential direction of the working member and, in contrast to a screw-compressor, so that their main direction joins with said circumferential direction.
  • the working spaces are situated at equal positions in the direction of the rotation axis of the working member and in the circumferential direction at intervals of an angle, which is the whole angle divided by the number of reacting members or by an integral multiple of it.
  • one revolution of the said member corresponds to one process cycle
  • one revolution of the working member corresponds to the number of cycles equal to the number of working spaces one after another.
  • the flow between the transferring space and the corresponding flow conduit may in practice occur through that opening in the body surrounding the rotation space of the working member, through which also the corresponding reacting member is extending into the working space in question.
  • the reacting member does not require work for its rotation, but is rotating freely.
  • the rotation of the reacting member is transversal in relation to the movement of the working member and working spaces moving therewith, and a higher pressure of the process space has effect only on a surface of the reacting member, which is a surface of revolution in relation to the rotation axis of the reacting member.
  • the former aspect means that the movement of the reacting member .does not positively alter the volume of the process space.
  • the latter aspect in turn means that a gas pressure difference cannot cause tangential forces upon the reacting member and thus no torque is created.
  • the rotation space of the working member has a cylinder-like general form.
  • Working spaces are then circumferentially situating channels in the working member.
  • One functional basic unit of a preferred embodiment is consisting of two working spaces one after another around the circumference of the working member, whence the said spaces are situating on the opposite sides of the working member symmetrically in relation to the middle axis. As the both side edges of the channel are at equal distances from the rotation axis of the working member, axial forces to the working member are avoided.
  • One functional unit of the embodiment mentioned is provided correspondingly with two reacting members situating on the opposite sides of the rotation space symmetrically in relation to the rotation axis of the working member.
  • the reacting member It is essential that in the invented machine it is possible to form the reacting member so strong that it is able to transmit outside the rotation space of the working member concrete forces caused by a pressure difference bet ween process and transferring spaces. Consequently, the machine may be used at high pressure level. It is possible to compensate reacting forces with a pressure effect programmed to be properly temporally variable during the process cycle.
  • the compensating force can be directed to an opposite surface of the reacting member, said surface being situated outside the rotation space of the working member.
  • One object of this invention is to provide a programmed compensation, in which in principle no energy is consumed. In one alternative embodiment there may be used several parallel working members with reacting members situated between them so that reacting forces compensate each other.
  • the reacting members can have end surfaces, which are surfaces of revolution in relation to the rotation axis of the reacting member, one end surface serving as a surface to form a partition wall and the other serving as a surface for pressure compensation.
  • the reacting members would then be continuous strong bodies, only somewhat thinner between said end surfaces and thus they could transmit reaction forces nearly in the direction of the rotation axis of the reacting member.
  • the partition wall forming part of the reacting member may be a plane surface, the normal of which is parallel to the rotation axis of the reacting member, or it may be a somewhat conical surface of revolution in relation to said axis.
  • the partition wall forming surface is provided with one transition sector with a minimum distance of edge line to the rotation axis of the reacting member. This transition sector may cover about 1/4 of the whole angle. In the remaining sector, covering about 3/4 of the whole angle, the distance of the edge line to the rotation axis of the reacting member has a constant maximum value.
  • the shape mentioned is advantageous in several respects.
  • the distance of the edge line from the rotation axis being constant, the corresponding clearance between the working member and the reacting member does not alter in consequence of errors in synchronization between movements of said members.
  • a small clearance and a reduced velocity together result in low gas leak through this leakage path.
  • the only part of the mentioned edge line, the corresponding clearance of which depends on the synchronization of rotating members, is a short part situated quite radially in relation to the rotation axis of the reacting member and having as its countersurface in the working member the end surface of the process space.
  • one object of the present invention is to provide a sealing member, which by a slight turning movement in relation to the reacting member can compensate errors in synchronization between the working and reacting members.
  • the movement of the sealing edge thus effected is practically identical with that caused by the rotation of the whole reacting member, whence theoretical possibilities even to an ideal sealing do exist.
  • the sealing member can also be constructed so that centrifugal forces do not influence its movement. Accordingly, required movements can be effected with an insignificant power consumption taking also in consideration the lightness of the member as well as a low absolute speed due to a small distance of movement needed.
  • a method for measuring precisely a momentary error in synchronization between the working and reacting members The possibility mentioned can be utilized when controlling movements of the sealing member in order to compensate errors in the said synchronization.
  • One essential demand, which this type of machine performing compression or expansion with minimal losses must fulfill, is that valve function must be carried out so that a dead space in front of a valve must be small enough. In the invented machine the dead space may be negligible.
  • the total area of the valve opening is of the same order as the maximal area of the partition wall corresponding to the area of a piston in a conventional piston machine.
  • the invented machine might be characterized by saying that a speed of the "piston" is constant but the area of the piston is different in different phases of process cycle.
  • the momentary areas of valve openings and the partition wall increase during the expansion cycle quite synchroneously beginning from value zero to certain maximal values of the same order. Accordingly, the velocity of gas in the valve opening need not rise essentially higher than the effective speed of the piston, thus resulting in small. losses in the valve opening.
  • Also during the closing period of the valve in expansion use only small losses result in the valve, since the closing action is rapid and the relative change of volume of the process space during said period is small.
  • a rotation axis of the valve is situated in a normal plane of the rotation axis of the working member, the plane of rotation being directed at least approximately towards the said axis of the working member.
  • Each of them is provided with a valve member, so constructed that it functionally corresponds to three true valve members one after another.
  • the total opening of the valves may be as large as on the whole is reasonable for diminishing pressure losses in said opening. Consequently, a circumferential speed of the working member is possible to keep as great as possible resulting in a minimum time of one process cycle and consequently in minimum leakage during one cycle.
  • a use of actual valves may be avoided by basing the valve function upon the rotational movement of the working member.
  • the working member itself closes the opening, which is situated in the body of the machine.
  • part of the reacting member which forms the partition wall has been shaped so that the edge line of the surface extends at one rotation sector farther off from the rotation axis of the reacting member, while the part of the working space corresponding to the mentioned sector extends so far in the direction of the rotation axis of the working member that only that portion extends to the position of the opening in the body of the machine.
  • One embodiment of the invention may result in even a very great pressure ratio.
  • the rotation space of the working member is provided with a projection portion surrounding the main portion of cylinderic form.
  • the partition wall part of the reacting member is then formed to extend only into said projection part during those periods when the valves are open.
  • the reacting member extends also into the main portion resulting in a large effective piston area and consequently in a great working volume.
  • a further object of the invention is to present how heat losses into the walls of the machine may be reduced to a small value.
  • Inner walls of the machine may be classified into two main categories. One group is characterized in that no precise dimensioning of walIs is necessary and that gas passing by the said surfaces has not temperature variation during a process cycle.
  • the surfaces mentioned may be provided with a heat insulation structure, the extreme surface of which is practically taking the temperature of the gas, whence heat exchange between gas and walls is small.
  • the walls participating in the formation of the process space are characterized in that precise dimensioning is required and also the temperature of gas varies during the process cycle. Certainly, in the preferred embodiment quite a low pressure ratio is used, resulting consequently in quite a moderate temperature variation only.
  • the temperature of gas is not high in the application in question, those surfaces may be kept e.g. at the mean temperature of gas, thus resulting in a net heat exchange between gas and walls to be zero. During each process cycle some amount of heat exchange to and fro then takes place, the phenomenon being quantitatively unessential, however. If the temperature of the gas is high, walls of the process space may be cooled beneath the mean temperature of the gas, e.g. to the temperature of the gas after expansion, or to a remarkably lower, value, even near ambient temperature without an excessive rise in heat losses.
  • One object of the invention is to present how also surfaces of the process space may be provided with an internal heat insulation layer and how even iron material may serve as an insulator. This kind of solution may become into question specially if very high gas temperatures were used. The surface of the insulation layer would then take some temperature between the mean temperature of gas and the internal temperature of structures surrounding the process space. The same construction may also be used if the temperature of working gas is considerably under ambient temperature.
  • Losses in bearings may be kept negligible, especially if a high pressure level is used in a closed process and at the most weights of rotating members are loading the bearings. Forces loading reacting members as well m as valve members may be compensated by means of a pressure effect, which may be arranged in a way which in principle does not consume energy at all. Possible mechanisms synchronizing the rotations of the working and reacting members cannot involve great power losses, because reacting members do not require work for their rotation. Also heat exchange between working gas and surfaces can be maintained small or negligible. The remaining loss factors are gas leak and pressure losses involved with the flow of working gas. These two loss factors are most essential also in the sense that the machine being connected as a component of a process, effects of losses of these types are reflected to operating circumstances of other machines of the process.
  • V R,opt
  • the minimum of losses would be independent of pressure, temperature and molecular weight.
  • use of light gases would result in a higher optimum speed and consequently in greater specific power.
  • the minimum of losses would be proportional to power 2/3 of the size of the relative clearance.
  • the 2/3-power relationship derived may be applied also to some known machines, as to a screw-compressor not using sealing lubrication.
  • Theoretical calculation as well as experience prove that losses are at least as great as in the best turbomachines.
  • the structure of the invented machine is so advantageous that there are reasons for using also the second or the third relationship presented for the minimum of losses for evaluating the merit of the machine.
  • one purpose of this invention is to set forth a machine, the clearances of which can be controlled during running for maintaining them at minimum values.
  • the merit of the machine most essential is the clearance which exists through the dominant part of time during operation, short term deviations having no significance from an energetic point of view.
  • a machine having a possibility to control clearances is superior as compared with machines with fixed clearances, the dimensioning of which must be made by considering a possibility of jamming in the most unfavourable combination of circumstances.
  • turbo-machines using a kinetic way of action are excluded, because then a very high gas velocity as well as narrow flow channels must be used. Losses depend on forming the channels and on a friction, factor which can be influenced only by the smooth ness of surfaces. Compression and expansion efficiencies in the best turbo-machines are 0.85-0.90 and possibilities for raising the efficiency are insignificant. Also positive displacement machines using sealing lubrication are excluded, because friction of oil is of significant order, in particular if speeds used correspond at least to a tolerable specific power.
  • a machine of positive displacement type not using sealing lubrication should fulfill the following conditions: 1) the size of clearances should not depend on a mutual synchronization of moving members, 2) the structure of the machine should be of the kind that members having effect on clearances do not bend in consequence of unsymmetrical gas forces, 3) lengths of sealing points in the direction of gas leak should be so great that the speed of leakage can be reduced, 4) clearances of the machine should be controlled during operation for keeping them at minimum values, 5) a cross-section area of the flow channel in the point of a valve function should be of the same order as in other parts of the working space, 6) opening and closing operations of the valve fuction should be rapid enough and 7) geometry of the working space should be advantageous so as to have a great cross-section area and a relatively short length in the direction of gas flow.
  • Condition 1 should be fulfilled before condition 4 could be applied because accomplishing a stable control system for regulating mutual movements of massive fast moving bodies with an extremely high precision is not possible.
  • the preferred embodiment of the invented machine is accomplishing the conditions presented as well as it is on the whole possible.
  • the reacting member of the machine includes a short portion of the edge line of the partition wall forming surface, the size of the clearance corresponding to it is dependent on the synchronization of the working and reacting members, but the geometry of the machine is so advantageous that the edge mentioned can be provided with a light sealing member capable to move in some extent in relation to the body of the reacting, member.
  • the problem of synchronization can be divided into two successive phases. Then for the rotation of the reacting member is required only a rough synchronization, and the actual sealing is accomplished by means of the sealing member, which need to move perhaps only a fraction of a millimetre in relation to the body of the reacting member.
  • the frequency of the movement may be high and never- theless the speed of movement as well as kinetic energy needed may remain low. Also the relative precision required for the movement is not high. Consequently, one possibility is to base the movement of the member on a prediction made on the ground of a precise measurement of error in. synchronization between working and reacting members.
  • the movement of the sealing member might be limited to the counter-surface situating in the working member. To prevent wearing a real mechanical touch may be avoided by using small gas streams conducted through the sealing member to some points of the sealing line. As the reacting member does not need work for its rotation, it is easy to maintain the speed of rotation usually perfectly constant.
  • movements of the sealing member are needed only if additional disturbancies occur, the influence of which cover a considerable part of the total operating time.
  • the control of clearances can be arranged to take place during operation, the machine being provided with temperature control systems for regulating temperatures of the members of the machine properly. Since the machine includes only a few members of quite unbroken masses, the temperature control can be accomplished by quite a small amount of control units. It is presented later in the specification, how the temperature control can be arranged even into the rotating members of the machine. As coefficients of thermal expansion in the case of metals are of the order of 10 -5 1/°C, a temperature change of 1°C means for a distance of 0.5 m a change of 5 ⁇ m in the corresponding clearance.
  • the control of clearances may surely be based on measuring temperatures of respective parts, at least if slow changes are taken into account by checking measurements at times, and subsequent adjustment of the control system.
  • sensors measuring directly clearances may be used as components of the control system.
  • the control may be alternatively based on local control of a sealing construction proper at least for some clearances of the machine.
  • the precision of the bearings of the machine is partly determining, how small clearances may be used.
  • precise bearings are very good. No forces in excess of those originating from the weight of a rotating member need to be directed to the corresponding bearing. If desired, even those forces may be compensated by a pressure force elsewhere than in the bearings determining the position of the rotating member. All rotating members are so firm that bending of the corresponding shaft at the point of the member is impossible and the bearings may be situated immediately on both sides of the member.
  • a use of temperature control systems eliminates a formation of free play in bearings due to uncontrolled thermal expansion. In all applications the essential structures of the machine can be kept near ambient temperature, whence e.g. precise roller bearings can be applied. On the other hand, if aerostatic bearings were used, a free selection of temperature would be possible. A good temperature control would secure small clearances and thus also a low energy consumption in the bearings.
  • a relative gas leak is proportional to the product of three factors namely clearance, speed of gas leak and time of process cycle.
  • clearance By maintaining clearances small, also leaking speed can be reduced efficiently.
  • the time of the process cycle is determined in the first hand by pressure losses in the valve, and also in this respect the invented machine is advantageous, because the cross-section of the valve opening is exceptionally large and opening as well as closing periods take place rapidly. Also the geometry of the working space is advantageous to result in a short time of process cycle.
  • the valve opening being large, it is possible to use as great circum speed as the quality of gas and temperature allow without the kinetic energy of gas also in other parts of the channel becoming of relative significance.
  • the invented machine should be used at some optimum circum speed, to which also the speed of working gas is proportional.
  • a numerical value of the optimum speed is dependent on gas, its temperature as well as clearancies of the machine, as presented earlier.
  • the optimum gas speed at the ambient temperature would be of the order of 50-100 m/s.
  • the speed would be so low that the relative significance of the kinetic energy of gas would be small, especially in the case of light gases, an optimum speed would be high enough to ensure quite a high volume flow.
  • a high pressure level is used, a high specific power results.
  • a higher speed than an optimum one may be used, thus resulting in a still higher specific power.
  • the machine for storing electric or mechanical energy the machine is applied as a component in a reversible process, which is operating during charging period in such a direction that by means of the process mentioned heat is removed from a cold store material.
  • heat must be put into the process.
  • Cold store material may be in solid or liquid form, or it may be air, which is liquefied during the charging period and correspondingly vaporized and released into atmosphere during the discharging period.
  • warm store in which water is serving as a heat storing material.
  • water is warmed up e.g. to 90-100°C and stored.
  • water is taken from the store and cooled in the process e.g. near the ambient temperature.
  • the remaining heat content of the warm store may be utilized as heat for certain low temperature purposes, as heating or water distillation. Due to exceptionally small losses of the invented machine, the efficiency of energy storing is good, especially as also the heat energy component is taken into account. Due to the reversible character of the process, requirements concerning small losses of 'machines are so severe that by using machines known before the efficiency attainable would be far too low.
  • Fig. 1 is a perspective view illustrating a possible general structure of the invented machine
  • Fig. 2 is a cross-sectional view of the machine taken along the line and in the direction of the arrows 2-2 of Figs. 1 and 3;
  • Fig. 3 is a partial sectional side view of the machine taken along the line and in the direction of the arrows 3-3 of Figs. 1, 2 and 4;
  • Fig. 4 is illustrating the circumference of the working member and the form of working spaces especially in the position of the separating wall and a location of valve openings in accordance with Figs. 2 and 3;
  • Figs. 5-6 are illustrating possibilities to arrange one true valve member to correspond to three virtual valves
  • Fig. 7 is a cross-sectional view taken along the line and in the direction of the arrows 7-7 of Fig. 2 and describing a valve member
  • Fig. 8 is a cross-sectional view describing a valve member taken along the line and in the direction of the arrows 8-8 of Fig. 7;
  • Fig. 9 is a cross-sectional view illustrating a counter-force part for arranging a pressure compensation onto the reacting member taken along the line and in the direction of the arrows 9-9 of Fig. 2;
  • Fig. 10 is a diagram describing a time course of pressure forces needed for a proper compensation of the reacting member
  • Fig. 11 is a cross-sectional view illustrating a device for altering periodically a pressure level in a pressure compensation cavity
  • Fig. 12 is an enlarged cross-sectional view illustrating a piston part of Fig. 11;
  • Fig. 13 is a cross-sectional view illustrating the piston taken along the line and in the direction of the arrows 13-13 of Fig. 12;
  • Fig. 14 is a cross-sectional view describing an auxiliary device used for accomplishing a pressure compensation of the reacting member
  • Fig. 15 is a fragmentary view illustrating a programmed shielding of a gas opening in the auxiliary device of Fig. 14;
  • Fig. 16 is a schematic side view of the machine illustrating locations of pressure compensators in connection with one reacting member
  • Fig. 17 is a diagram describing a time course of pressure forces needed for a proper compensation of a valve member
  • Fig. 18 is a schematic end view of the machine illustrating locations of pressure compensation in connection with valve members relating to one process space;
  • Figs. 19-21 are illustrating a possibility to form the constant-radius-edge of the partition wall forming part of the reacting member so that the corresponding clearance has a considerable length in the direction of gas leak;
  • Fig. 22 is illustrating a possibility to use a labyrinth seal for reducing gas leak through the clearance in accordance with Figs. 19-21;
  • Fig. 23 is a side view of a sealing member mounted to a radial-like edge of the partition wall forming surface of the reacting member taken along the line and in the direction of the arrows 23-23 of Fig. 24;
  • Fig. 24 is a cross-sectional view of the sealing member taken along the line and in the direction of the arrows 24-24 of Fig. 23;
  • Fig. 25 is a schematic view illustrating supplying high pressure gas into sealing members in the reacting member
  • Fig. 26 is a sectional side view of a. continuously controllable sealing member taken along the line and in the direction of the arrows 26-26 of Fig. 27 as well as of Fig. 28;
  • Fig. 27 is a cross-sectional view of the sealing member taken along the line and in the direction of the arrows 27-27 of Fig. 26;
  • Fig. 28 is a cross-sectional view of the sealing member taken along the line and in the direction of the arrows 28-28 of Fig. 26;
  • Fig. 29 is illustrating a structure of a programmed plate in connection with an optiocal position defining system of the sealing member
  • Fig. 30 is illustrating a structure of a receiving device co-operating with the plate of Fig. 29;
  • Fig. 31 is a block diagram illustrating a control of the sealing member
  • Fig. 32 is a cross-sectional view of a valve controlling a passage of high pressure gas for effecting turning of the sealing member taken along the line and in the direction Of the arrows 32-32 of Fig. 33;
  • Fig. 33 is a sectional side view of the valve controlling the sealing member taken along the line and in the direction of the arrows 33-33 of Fig. 32;
  • Fig. 34 is a fragmentary circumferential view illustrating a control of an effective gas opening taken along the line and in the direction of the arrows 34-34 of Fig. 32;
  • Figs. 35-36 are schematic views illustrating an optical measurement of error in synchronization between the working member and the reacting member
  • Fig. 37 is an enlarged schematic view illustrating co-operating members of the measuring system taken along the line and in the direction of the arrows 37-37 of Fig. 35;
  • Fig. 38 is an enlarged fragmentary view illustrating positions of supplying and receiving optic cables taken along the line and in the direction of the arrows 38-38 of Fig. 37;
  • Fig. 39 is an enlarged fragmentary view illustrating the structure of the measuring system on the position of a light absorbing slit taken along the line and in the direction of the arrows 39-39 of Fig. 37;
  • Fig. 40 is a sectional view illustrating the location of the active part of the system defining an error in synchronization between the working member and the reacting member taken along the line and in the direction of the arrows 40-40 of Fig. 41 ;
  • Fig. 41 is a side view of the active member of an optical measurement system taken along the line and inthe direction of the arrows 41-41 of Fig. 40;
  • Fig. 42 is illustrating schematically a possibility to use distant photo-detectors and light transmitting optic cables
  • Fig. 43 is illustrating an arrangement, according to which light can be supplied into the reacting member from a stationary light source and electric contacts are arranged through the shaft;
  • Fig. 44 is a schematic view illustrating arrangements for the sealing members concerning supplying high pressure gas as well as electric and optic connections needed;
  • Fig. 45 is a block diagram illustrating a temperature system, in which the member in question has been divided into several parallel parts, which are individually controlled;
  • Fig. 46 is a sectional view illustrating an arrangement for achieving heat exchange conduits near a surface of a member to be thermo-regulated
  • Fig. 47 is a sectional view illustrating a structure of a straight labyrinth seal
  • Fig. 48 is a diagram illustrating a decrease of gas leak as a function of a number of labyrinth grooves one after another;
  • Fig. 49 is a sectional view illustrating a heat insulation structure suitable for surfaces of which precise dimensioning is not needed;
  • Fig. 50 is a top view of a heat insulation structure suitable for surfaces requiring a precise dimensioning taken along the line and in the direction of the arrows 50-50 of Fig. 51;
  • Fig. 51 is a sectional view of the heat insulation structure taken along the line and in the direction of the arrows 51-51 of Fig. 50;
  • Fig. 52 is a fragmentary top view of a heat insulation structure suitable for use in connection with working gas under the ambient temperature
  • Fig. 53 is a schematic sectional side view of an alternative general structure of the invented machine.
  • Fig. 54 is a graphical diagram illustrating a time course of various quantities in the invented machine during one process cycle
  • Fig. 55 is a block diagram indicating auxiliary devices associated with one machine unit
  • Fig. 56 is a partial sectional side view of one alternative embodiment of the invented machine.
  • Fig. 57 is illustrating the circumference of the working member in the embodiment of Fig. 56 analogously to Fig. 4;
  • Fig. 58 is a partial sectional side view of still another embodiment of the invented machine.
  • Fig. 59 is illustrating the circumference of the working member in the embodiment of Fig. 58 analogously to Fig. 4;
  • Fig. 60 is a schematic cross-sectional view of the machine in accordance with Figs. 58-59 as to parallel functional units are used in order to compensate reacting forces;
  • Fig. 61 is a process diagram illustrating the use of the invented machine as a component in a heat power process using Brayton-cycle
  • Fig. 62 is a block diagram of a substitute model corresponding to a real expansion machine
  • Fig. 63 is a block diagram of a substitute model corresponding to a real compression machine
  • Fig. 64 is a graphical diagram illustrating the process efficiency of the process according to Fig. 61 as a function of the maximum gas temperature as various loss parameters have certain numerical values;
  • Fig. 65 is a process diagram illustrating a charging period of an energy storing process, in which the invented machine is used as a component;
  • Fig. 66 is a process diagram illustrating a discharging period of an energy storing process, in which the invented machine is used as a component;
  • Fig. 67 is a process diagram illustrating a cold store part of the energy storing process, if liquid cold store material is used;
  • Fig. 68 is a process diagram illustrating an alterna tive cold store part of the energy storing process, as liquid cold store material is used;
  • Fig. 69 is a process diagram of the energy storing process, if the cold store side of the process is based on liquefying air;
  • Fig. 70 a partial process diagram illustrating a modification of the process shown in Fig. 69;
  • Fig. 71 is a block diagram of a substitute model corresponding to a real ambient temperature machine in Fig. 65;
  • Fig. 72 is a block diagram of a substitute model corresponding to a real low temperature machine in Fig. 65;
  • Fig. 73 is a graphical diagram illustrating the process efficiency of the storing process of Figs. 65 and 66 as a function of a momentary cold store temperature, as various loss parameters have certain numerical values.
  • Fig. 1 is illustrating a possible general structure of the invented machine.
  • the machine includes a power shaft 2 connected to a working member situated inside the the body 4 of the machine.
  • the machine includes two functional basic units 40 one after another in the direction of the shaft 2 on the positions of halves 4a and 4b of the body.
  • a torque of the whole machine may be fairly constant within each process cycle.
  • Assembling of the machine may be carried out by pushing halves 4a and 4b of the body towards each other axially and by attaching them by means of projecting flanges 41.
  • Each functional unit includes two reacting members situated at a transverse position in relation to the working member on opposite sides thereof. Shafts 9 of said members being shown in Fig. 1.
  • a synchronizing mechanism 42 may be used between corres ponding shafts 2 and 9.
  • the shafts 9 of the reacting members may be provided with small motors 43, whence a main energy exchange may occur between the motor and the. reacting member, thus avoiding stresses and wear of the synchro nizing mechanism. It might even be possible to manage without said mechanism, if an elctronic control of motors 43 were safe enough.
  • Valve members belonging to the machine are rotated by means of shafts 24 and 25. The rotation may be arranged by using motors 39 attached to the corresponding shaft.
  • flow conduits 18 and 19 which have been branched for the both functional units 40. In expansion use gas enters the machine along conduit 18 leading to the valve members, and returns along conduit 19, the direction of circulation being reversed in compression use.
  • FIGs. 2-3 An internal structure of the machine is illustrated in Figs. 2-3.
  • the rotation space 3 of the working member 1 situated inside the body 4 of the machine has in the example the general form of a cylinder, the working member being attached directly to the power shaft.
  • the working member 1 is formed so that in the rotation space there are two working spaces 5 one after another in the direction of the circumference of the working member, said spaces being situated symmetrically on opposite sides of the working member.
  • the functional unit described also includes two reacting members 8, which situate transverse in relation to the working member and on opposite sides of it. As an expansion or compression process takes place in the same phase in the both working spaces of the functional unit, no transverse reacting forces are effecting the shaft of the working member.
  • both side edges of the working space are at the same distance from the rotation axis of the working member, whence no axial forces originated from gas pressure are created. Accordingly, the corresponding bearings are loaded only by the weight of the working member and the power shaft.
  • the shafts 9 of the reacting members are located in the same plane to the rotation axis of the working member. Additionally, said members are located so that their rotation axes are situating outside the rotation space 3 of the working member. It would also be possible to use modifications where the shafts of the reacting members were mounted to deviate somewhat from the normal plane of the power shaft.
  • one functional unit might include n reacting members, where n is any positive integer. In that case the unit might include correspondingly n working spaces one after another circumferentially at intervals of the angle 360o/n. In principle, the number of working spaces might be alternatively m-fold as compared with the number of reacting members. Then only a fraction of 1/m of all working spaces would be simultaneously on the points of reacting members and thus in active use.
  • a partition wall 15 (indicated by a dotted line) formed by the reacting member 8 divides the working space 5 into two parts, of which the process space 6 is connected to the corresponding flow conduit 18 through openings 26 in the body of the machine.
  • the other partial space 7, named in the following a transferring space, is continuously in connection with the corresponding flow conduit 19 through an opening 52 in the body structure 4 surrounding the rotation space of the working member.
  • the reacting member 8 is extending into the working space 5 thus forming said partition wall 15.
  • the partition wall forming surface 10 of the reacting member must be a surface of revolution in relation to the rotation axis of the reacting member.
  • Said surface may be a plane surface, the normal of which is parallel to the rotation axis of the reacting member or it may be a somewhat cone-like surface of revolution in relation to the said rotation axis for reasons explained later.
  • the shape of the edge line of the partition wall forming surface 10 has been presented in Fig.3, said line having portions 44, 45, 46 and 47.
  • the partition wall forming part is thus provided with one transition sector 77 having a sector angle ⁇ which in the example is about 90°.
  • the partition wall 15 is formed by that changing part of the partition wall forming surface 10 which, in course of the rotation of the reacting member in turn is inside the rotation space 3 of the working member.
  • a general form of the edge line of the partition wall forming surface 10 may be defined by means of the radial co-ordinate r and the co-ordinate ⁇ r so that as the angular co-ordinate is varying beginning from the sector 77, which is turned towards the working member the process cycle changes to a direction corresponding to the order of arrival of differentpoints of the said edge line in expansion use into the rotation space of the working member, the radial co-ordinate is growing relatively steeply (segment 44) to a constant value r 1 , remaining at that value for the most part of the angle change corres ponding to the whole circle and returning finally (segment 46) to a low starting value r 0 near the completion of the whole circle.
  • the described general form may be superimposed by local deviations, as projections or grooves.
  • Most essential from functional point of view is that the distance of the edge line from the rotation axis of the reacting member is constant for the long segment 45 of the edge line.
  • the clearance 14 corresponding to the said segment 45 remains constant irrespective of errors in synchronization Accordingly, it is possible to maintain said clearance 14 small. Faults in synchronization are harmful only as far as the segment 44 of the edge line is concerned.
  • This segment 44 going quite radially is relatively short and is in the rotation space of the working member only for part of time, whence gas leak through the corresponding clearance 13 remains quite small.
  • a radial-like direction of the last mentioned edge 44 is advantageous for providing said edge with a special sealing member, as presented later.
  • the segment 46 of the edge line corresponding to the transferring space end of the working space is not essential as to leakage, because there is no pressure difference between process and transferring spaces when said segment is inside the rotation space.
  • Fig. 3 also a location of valve members 23 is sketched.
  • Shafts 24 and 25 of valve members are located in a certain normal plane of the rotation axis of the working member, this normal plane not being the same in which the shafts 9 of the reacting members are situated.
  • the plane of rotation of each valve member may be directed at least approximately towards the rotation axis of the working member.
  • the rotation space of the working member may at the position of valve openings 26 deviate from a cylinderic general form in a way presented in Fig. 3.
  • the rotation space includes a ring-shaped projection part 48 around the cylinderic main part, said part 48 being formed by a channel in the body of the machine.
  • the bottom 49 of the channel is formed to correspond to the form of an unbroken circum surface 99 (Fig. 2) of the valve members- as well as it is possible, as presented later in detail.
  • Fig. 4 is presented a part of the circum surface of the working member by using as co-ordinates the rotation angle ⁇ w of the working member and the axial distance z w in the direction of the rotation axis of the working member.
  • the figure shows a separating wall 21 between two working spaces 5.
  • One functional unit includes two separating walls 21 situated symmetrically on the opposite sides of the working member.
  • Fig. 4 are also presented locations of valve openings 26 at a moment when the partition wall 15 in relation to the working space is in the position shown in figure corresponding also to the situation in Figs 2-3.
  • the separating wall 21 is acting as a sealing wall between two working spaces one after another.
  • said wall is provided with a projection part 50 corresponding to the form of the cross-section of the channel 48.
  • the projection part 50 of the same continuous material as the main body of the working member, if the body 4 of the machine is provided with a groove 51 situated in the inner wall of the body in the direction of the rotation axis of the working member and at a sector corresponding to the opening 52 for the reacting member.
  • the projecting part 50 can be guided through said groove 51.
  • the gas openings in the body of the machine have thus to be located, as seen in the direction of the rotation axis of the working member, at the point corresponding to that side of the working spaces running circumferentially, on which the extreme end 20 of the process space 6 is situating, and as seen circumferentially on the process space side, at least one opening extending beside the point where the partition wall is formed.
  • the valve members 23 start to open at a moment when the corresponding opening has been fully shielded by the separating wall 21 thus preventing gas leak into the extreme end 22 of the transferring space of the adjacent working space.
  • valve opening It is possible to achieve a large total area of a valve opening, if it is used several openings 26 one after another circumferentially, one of the openings extending close by the point of the partition wall, and each opening being provided with a real valve member, said valve members being located fan-like so that their planes of rotation are directed at least approximately towards the rotation axis of the working member.
  • the shafts of the valve members may be interconnected by universal joints thus making it possible to rotate the whole chain of valves by means of one shaft connected to the last valve member.
  • each virtual opening may be started when the corresponding virtual opening has come into the shield of the separating wall 21.
  • the width of said virtual openings is small in the direction of the ⁇ w -axis, it is possible to manage with a relatively narrow separating wall, whence more useful working space may be achieved. Opening of valves may take place in the shield of said separating wall so that when extreme end 20 of the process space comes to the position of the opening in question, it is already fully open.
  • the use of virtual openings is advantageous, in addition to simplifying structures and increasing working volume, also because then it is possible to manage with only one wall 38 between the true openings 26. As it is seen from Fig. 54, which is explained later, such a wall has a tendency to delay increasing of the total area of valve openings.
  • Sealing along the outer sides G-H, H-J, I-J and I-G is achieved by forming the projection par 50 of the separating wall to correspond to the crosssection of the channel 48.
  • the forms of the bottom 49 and the unbroken circum surface of the valve correspond at all points to each other so well that dead space between them has no practical significance.
  • Figs. 2, 7 and 8 are illustrating a construction of rotating valve members 23.
  • they are bodies of revolution with the exception that from a certain sector material has been removed so that when this sector is turned towards the gas opening 26, a connection between the process space 6 and the corresponding conduit 18 is effected.
  • virtual openings 27a-c in succession in time with their arrival at the position of the separating wall 21, opening times of the individual virtual openings are different from each other.
  • the opening 28 in the valve is formed of three sections in the direction of the axis of the valve, said sections having individual opening anglesß a , ß b and ß c as seen from the axis of the valve.
  • the individual edges 29 a-c are acting as front edges, whereas the other edges 30 are all in the same line resulting in a simultaneous closing of all virtual openings in expansion use and correspondingly in a simultaneous opening in compression use.
  • Simultaneous actions during said phases are advantageous in making the corresponding periods as short as possible for avoiding losses.
  • the same point of view prefers a small visual angle ⁇ of the opening 26 in relation to the axis of the valve. In the example this is about 30o, whence losses during the periods mentioned are no more dominating.
  • one revolution of the valve corresponds to one process cycle.
  • the valves have been provided with supporting parts 32 having the form of a body of revolution.
  • Fig. 7 also presents a possibility to use a shielding part 35 to reduce heat exchange between gas and the circum surface of the valve.
  • Passage 36 of gas may take place e.g. in conformity with Fig. 8 past the valves along channels 37 in the body of the machine.
  • the total cross-section area of those conduits is possible to dimension greater than the total area of gas openings 26, whence pressure losses in these conduits are not significant.
  • the scope of the invention also includes an alternative in which the reacting members and/or valve members are formed so that one revolution of said members corresponds to two process cycles.
  • the members have two gaps 77 and 28, respectively, symmetrically on the opposite sides of the member in question.
  • the advantage achieved is geometrical symmetry in relation to the rotation axis, resulting in an inherent balancing of the member.
  • the drawback involved is greater losses than in the embodiment presented.
  • the balancing of said members in the preferred case may be accomplished by planning the members so that on the sides opposite to gaps 77 or 28 some material is removed from suitable areas unessential from a functional point of view. Radially going gaps 102 in Fig. 7 serve the purpose mentioned.
  • the power shaft 2 may be composed of two parts, which are provided with a thicker portion 76 for mounting the shaft halves into the ends of the working member so that even a very great torque can be transmitted.
  • a connection may be arranged e.g. by using round locking means 79, as indicated in Fig. 2.
  • the reacting members may be firm bodies as in Fig. 2 and capable to transmit even very great forces caused by a pressure difference between the process space and the transferring space outside the rotating space of the working member. Reacting forces may be compensated by a programmed pressure effect which is directed onto a counter-surface 11 in the reacting member, said surface being situated outside the rotation space 3. Bearings 67 and 68 may take forces due to incomplete pressure compensation. The bearings can be dimensioned to bear for a short period the whole reacting force during a possible failure in pressure compensation. Mounting of the reacting member may happen so that the shaft 9 is pushed through a separate ring-like part 64 and screwed into its place and locked in tangential direction by using a Locking part 66.
  • the machine is looked in the direction of the shaft 9 and the location of the total cross-section area 60 of the working space is indicated by a dotted line.
  • the resultant of counter-forces can be kept every moment at the same line parallel to the axis of the reacting member as a momentary centre of gravity of the partition wall 15.
  • the locus 59 of the centre of gravity remains inside a triangle determined by the gravity centres 56-58 of the cavities, it is possible to arrange the resultant of forces to follow said locus.
  • curves of forces F 54 -F 55 they are of periodic form deviating from a sinusoidal one mainly so that they have flattened portions at both tops of the curves, whereas the curve for F 53 has one long flattened portion.
  • a periodic variation of pressure may be accomplished by a periodic variation of volume by using a suitable apparatus in connection with each cavity. Accomplishing a back-and-forth variation of volume does not in principle consume energy. If the volume of compensating cavities is of the order of 1% of the corresponding working volume of the machine, losses in actual compensating devices may be at the most some thousandth parts of the power of the machine.
  • the apparatus 70 includes a reciprocating piston 71 inside a tubular housing 82 and provided with support bearings 80, 81.
  • the piston is moved by a conventional crankshaft 73 provided with a flywheel 74 and an electric motor 75.
  • a space 72 in connection with the corresponding cavity 55 In front of the piston is a space 72 in connection with the corresponding cavity 55.
  • the work done to the piston during expansion of the space 72 is stored into the flywheel and possibly also in electric form by using the electric machine 75 as a generator. Synchronization with other moving parts of the machine is possible to arrange by using an electronic control of the motor 75.
  • Pressure p min is that existing in the conduit 19 corresponding to the transferring space.
  • Pressure p max may be e.g. 1.3 p 1 , where p 1 , is the pressure in the conduit 18 corresponding to the process space.
  • a suitable pressure may be produced by using a conventional compressor as an auxiliary device.
  • the apparatus described is suitable for achieving curve forms F 54 and F 55 .
  • the space 83 may be omitted and the space 84 dimensioned to cover a dominant part of the process cycle.
  • the device 90 includes a rotating valve member 91 provided with circumferential slots 97 and 98 at the position of openings 93 and 94 in the wall 92 of the device.
  • the slots are designed properly to result in a desired time course of the size of openings between the hollow interior 100 of the valve member. and the corresponding conduits 95 and 96 having pressure p high and p low . Said interior is in connection with the cavity 55 in question.
  • the rotating valve member 91 shuts in course with time a variable portion of the openings as described in Fig. 15.
  • the rotation of the valve member 91 is synchronized with movements of other parts of the machine by controlling electronically the motor 101.
  • the device described may he used so that more gas enters the cavity through the conduit 95 and the amount of gas is diminished through the conduit 96.
  • the device can be used also so that there are sever pressure levels available to minimize energy consumption.
  • Fig. 16 is illustrating locations of compensating devices as seen from outside of the machine in the direction of the shaft 9 of the reacting member. Locations of the counter-force part 63 as well as of cavities 53-55 are indicated by broken and dotted lines, respectively. Reference signs are indicating positions of devices 70 and 90 described in Figs. 11-15. Each cavity is provided with one main device 70 and one auxiliary device 90. Possibly remain- ing unbalanced forces load the bearings of the reacting member. These forces remain so small that even very great pressure levels may be used in a closed process. Mounting holes 69 for the main device 70 are shown in Fig. 2.
  • the curves are periodic having flattened portions at both tops. Thus, the forces may be approximately compensated by using devices 70 and 90 described above.
  • Fig. 18 indicates positions of compensating devices for the valve members as seen from outside the end side of the machine in the direction of the power shaft, the location of contours of valves 23 being indicated by dashed lines. Reference signs are those used in Figs. 11-14. Compensating devices are mounted into corresponding holes 108 and 109 indicated in Figs. 2 and 7.
  • Figs. 19-21 illustrate a possibility to achieve for a leak path 14 corresponding to that segment of clearance between the working member and the reacting member which is independent of synchronization, so great length in the direction of leakage that speed of leak can be reduced.
  • the best possibilities to accomplish this are present if the partition wall forming surface 10 is situated at the position of that normal plane of the axis of the reacting member which extends through the axis of the working member, whence a tangent of the bottom of the working space in circumferential direction is parallel to the axis of the reacting member.
  • the rim 45 of the reacting member may in accordance with Fig. 22 be provided with transverse grooves 62 forming a labyrinth seal structure 103.
  • the grooves may be interrupted to avoid gas leak in the direction thereof.
  • the general form of the rim may be that described in Figs. 19-21.
  • Figs. 23-24 describe one embodiment for providing the radial-like edge of the reacting member with a sealing member 110 forming the true edge 44.
  • the sealing member may turn in some extent in relation to axles 112 which are at least approximately parallel to the edge 44.
  • the sealing member may be mounted so that axles 112 are pushed in their holes 113 axially into their places after insertion of the sealing member.
  • the turning movement of the sealing member is restricted by an extension part 114 located in a cavity 115 of the body 111 of the reacting member.
  • the sealing member is constructed somewhat unsymmetrical so that a centrifugal force turns said member to its outmost position shown in the figure, whence the extreme edge 44 is situating at a surface 117 which is an extension of the partition wall forming surface 10 of the reacting member.
  • the sealing member is at the position described.
  • the member may be turned inwards by applying gas pressure against the extension part 114 through a conduit 116. This may be done during starting and stopping of the machine as well as during special disturbances.
  • the clearance 13 between the edge 44 and the counter-surface 119 in the working member may be maintained quite small for a dominant part of time. For that purpose it may be used e.g.
  • Gas leak through a clearance 122 between the sealing member 110 and the body 111 of the reacting member is negligible, because the clearance is formed between surfaces 123 and 124, being surfaces of revolution, and the radius of the sealing member is small. According to 23 it is possible to use gas pressure to support the sealing member through cavities 120 during periods when the position of the sealing member is changed.
  • High pressure gas needed in conduits 116 and 121 may supplied into the reaction member through the rotation axis as described in Fig. 25.
  • Valves 125 and 126 controlling the gas flow may then be situated in connection with the stationary body of the machine. Opening and closing of valves may be timed so that gas support through cavities 120 is always effecting during turning of the sealing member.
  • the total edge 44 may be provided with two sealing members 110 one after another, corresponding to two straight portions of said edge.
  • a continuous curved form of the edge 44 the form being selected to correspond to the cross-section of the projection part of the separating wall in the working member.
  • the radius of the sealing member is selected to be different in different positions along the direction of the axle 112 so that the desired form is resulting at an intersection of the circum surface 123 and the surface 117.
  • FIG. 26 shows a sealing member corresponding to one straight portion of the edge 44.
  • the direction of axles 112 differs slightly from the direction of the sealing edge 44 so that the circum surface 123 of the sealing member is a cone-like surface of revolution in relation to the axle 112, said surface is a tangent surface to a surface 117 imagined as an extension of the partition wall forming surface 10 of the reacting member.
  • the sealing line 44 as well as the clearance 13 between the sealing member 110 and the counter-surface 119 are formed approximately at the point of the mentioned tangent line, because the sealing member is formed thinner on the side being outwards from the reacting member so that the surface 118 beginning from the sealing edge is situating nearer the axle 112 than the cone surface 123.
  • the degree of conical form is such that the distance R s of each point of the sealing line from the axis of the sealing member is proportional to the distance R r of the point in question from the rotation axis of the reacting member. If the turning angle ⁇ of the sealing member remains small, the movement of the sealing edge 44 caused by the turning of the sealing member is identical to that achieved by a rotation of the whole reacting member.
  • forms of the cone surface 123 and the countersurface 124 are identical, gas leak through a narrow and long clearance can be kept negligible.
  • the sealing member may be formed symmetrical so that its centre of gravity is located exactly at the axis of rotation, whence a centrifugal force does not cause a torque to said member, even if the direction of axles 112 is different from the radial direction of the reacting member.
  • the centre of gravity may be located slightly unsymmetrical so that the sealing member has a tendency to turn to the middle position described in Fig. 27.
  • the turning of the sealing member may be achieved by using a projection part 127 serving as a piston and a cavity 128 serving as a cylinder.
  • the cavity is on the side of the body 111 of the reacting member.
  • the ends of the cavity are provided with gas conduits 129 and 130, through which high pressure gas is effecting the piston and leaking away through clearances of the piston-cylinder construction.
  • a knowledge about the momentary position of said member is needed.
  • the sealing member is provided with a measuring projection 131 having a measuring hole 132 provided with a plate 133 having properly designed openings for arranging an optical position determination in digital form.
  • a good resolution is achieved.
  • a cable 172 connected to said unit may be an optic cable receiving light through the plate 133 and transmitting it to a detector situated near the axis of the reacting member, or the cable mentioned may be an electric cable leading to local photo-detectors within the receiving unit 134.
  • An optic cable 135 is supplying light to the measuring point from a distant light source, which may be situated outside the rotating reacting member, as described later.
  • the cable may consist of several fibres 173 arranged at the end of the cable properly for the purpose.
  • FIG. 29 is illustrating one opening arrangement of the plate 133.
  • a momentary position of the sealing member is defined by using two digits. The less significant one is revealed by using round openings 136 and the more significant by using elongated openings 137.
  • the receiving unit 134 according to Fig. 30 is provided with receiving openings 138a-c for the less significant digit and openings 139a-d for the more significant digit.
  • Members 140 behind the openings 138-139 may be the ends of optic cables or local photo-detectors. The dimensioning of openings being such that light is going at each moment through one or two openings 136 into the corresponding receiving means, a resolution of 41 positions is achieved. In the case of Fig. 29 light is going through openings 138a, 138b, 139b and 139c.
  • Fig. 31 is a block diagram illustrating a regulation of movements of the sealing member.
  • High pressure gas in the conduit 141 is distributed properly into the conduits 129 and 130 by using a valve member 142 controlled by an electronic control unit 143.
  • Information about the momentary position of the sealing member is received from the measuring unit 144 described above in connection with Figs. 26-30.
  • the unit 145 indicates a momentary error in synchronization between the working and reacting members, as described later in connection with Figs. 35-43.
  • valve 142 is connected through an electric cable 175 to a central control unit and mounted into a space
  • the valve includes a moving part
  • Gas coming into a hollow interior 151 has an access through slots 152a-d in the circumferential wall 155 of the moving part 147 into conduits 129 and 130 through suitably formed openings 153a-d in the body 154 of the valve. Openings 153a and 153c situated at opposite sides are connected to the conduit 130 and correspondingly openings 153b and 153d to the conduit 129.
  • the openings have triangular formes described in Fig. 34.
  • a precise and immediate determination of error in synchronization between working and reacting members may be based on the fact that a certain point in the constantradius-edge 45 of the reacting member follows a certain track on the bottom of the working space.
  • the error optically by using co-operating members situated at said edge 45 and at some point in the working member along said track.
  • Figs. 35-36 it is illustrated how by using an active measuring member 156 at the circumference of the reacting member it is arranged two measurements for each process cycle by using two co-operating members 157 being situated at the same distance from the axis of the working member.
  • another measuring member 156 on the opposite side of the edge 45 it would be possible to achieve e.g. four measurements for each rotation of the reacting member.
  • the cooperating member is a passive one which reflects back light coming from the member 156.
  • the active member has effectively a multiplicity of light source - light detector pairs.
  • the passive member is provided with a slit 158 which does not reflect light back to the active member 156.
  • the direction of the slit has an angle of in relation to ⁇ w expressing the direction of the circumferential movement of the member 157.
  • the member 156 moves in direction ⁇ r . The angle is selected so that the relationship is valid, where v w and v r are corresponding circum speeds.
  • the same source-detector pair remains on the point of the slit all the time the co-operating members cross each other.
  • the time of light pulse is long enough to ensure a response in other detectors in spite of great circum speeds and small dimensions of detectors.
  • a precision corresponding to a fraction of a space between adjacent measuring points can be achieved if also relative light intensities are measured in each detector.
  • a precision of 20-30% in intensity measurement would already mean an essential improvement.
  • true light sources or deterctors are not in the measuring member 156 itself, but light enters and leaves said member through optic cables 161 and 162.
  • a real light source may be situated outside the reacting member, as explained later in connection with fig. 43.
  • the location of the detector unit may be near the rotation axis of the reacting member.
  • Figs. 38-41 illustrate a structure of the measuring member 156.
  • the ends of light cables 161 and 162 are mounted at positions of holes 159 and 160.
  • the width of the slit may be made very small if the reflecting member 157 is manufactured of two pieces attached together.
  • the measuring member may have a collar part 164, by means of which centri fugal forces are transmitted into the body of the reacting member.
  • the measuring member may be mounted through an opening 163 in the partition wall forming surface 10. After mounting said opening is closed by a corresponding cover.
  • Light cables 161-162 are extending in a cavity inside the reacting member to a vicinity of the axis of the reacting member, where the corresponding light dectectors 165 may be situated, as described in Fig. 42.
  • a light source unit 167 may be situated in connection with the stationary body of the machine and light is transmitted through a cable 166, the other end of which is situating coaxially at the end of the shaft 9 of the reacting member.
  • three sliders 168 and a corresponding electric cable 169 it is possible to arrange an electric supply to devices inside the reacting member and further to transmit control orders and other information between the rotating member and the stationary body. By utilizing known electric methods three sliders are sufficient for purposes mentioned, although a transmission of a multichannel information is concerned.
  • Fig. 44 is shown how through an axial conduit 174 high pressure gas from the stationary body may be supplied into conduits 121 and 141 for purposes of sealing members 110.
  • Light from an optic main cable 166 may be distributed into cables 135 and 161 presented in Fig. 26 and Fig. 38, respectively.
  • It is also presented, how electronic circuits needed may be concernated into an electronic unit 170 situating near the rotation axis of the reacting member.
  • the unit 170 may be mounted into its place through a channel 171 situated radially in the body of the reacting member. If the wall of the gas conduit 19 is provided with a small door (not shown), the mounting may happen handy.
  • Electric connections to cables 169 and 175 may be arranged by using suitable contact plugs.
  • Optic detectors relating to light cables 162 and 172 may also be situated in the electronic unit 170.
  • Fig. 3 how the working member is provided with a network 176 for circulating heat exchange gas.
  • the circulation takes place through a conduit 177 leading to the end space 178 and a conduit 179 connected to the space 180 at the circumference of the working member.
  • the mounting channel 51 may be closed after mounting of the working member by a suitable part 181.
  • FIG. 3 is also shown, how by using conduits 182 as well as spaces 183, a heat exchange circulation through the reacting member may be arranged, the end surface 10 of said member being provided with several holes, which are situated at certain intervals at a constant distance from the axis of the reacting member.
  • gas pressure in the temperature control circuit is maintained the same as that in the working gas surrounding the reacting member, gas leak can be kept small.
  • Spaces 183 in the wall of the stationary body of the machine may be surrounded by local labyrinth seal.
  • An arrangement of heat exchange circulation into valve members is illustrated in Figs. 3 and 18.
  • the pressure level in conduits 184 may be the same as that of working gas in the valve space, whence gas leak can be kept small.
  • Main conduits leading to each member are distributed into several branches. By careful planning a distribution of heat exchange may be made proper for resulting in a sufficiently uniform temperature within the body of each member. Temperature level may then be controlled e.g. by regulating total mass flow circulating through each member. The regulation may be based on temperature measurements with electric sensors located within the member in question. From a rotating member measurement information may be transmitted into a stationary control unit e.g. as described in connection with Fig. 43.
  • the state of the art in electronics and control technics further permits even providing each member with several branches which are individually controlled. This has been illustrated schematically in Fig. 45. Parts being situated inside a rectangle 185 are within a rotating member. In the stationary part of the machinery is located a pump 186 for gas circulation as well as a heat exchanger 187. The flow conduit 188 is divided inside the rotating body into branches 189. The amount of average gas flow is controlled by valve means 190. A circuit connected to each valve consists of at least one temperature sensor 191 and an electronic control circuit 192.
  • the state of the art permits a use of small and unexpensive control components, whence even numerous control circuits may be used in each part of the machine.
  • control unit may be situated inside a thermally insulated casing, inside which a part of cooling circulation is conducted.
  • the structures may be kept at a low temperature level even if hot working gas is used, as discussed later.
  • Supplying energy into a rotating member may be arranged also otherwise than by feeding along the corresponding shaft. It is possible to use a winding inside a rotating member, which is passing through a magnetic field created by means being situated in the stationary body of the machine. It is also possible to use circulating heat exchange gas for rotating a small generator. For transmitting information also wireless methods may be used, e.g. optical technics.
  • a total dimensioning of the machine may be such that during running the temperatures of the rotating members are maintained somewhat higher than that of the stationary body of the machine. Thus during running smaller clearances appear than in an isothermal case.
  • the heat exchange network needed in each member may be arranged e.g. in connection with casting procedure. If the member in question is composed of several parts united by welding technics, the conduits needed can be easily arranged. If it is desired to use conduits going very near the surface, an arrangement described in Fig. 46 may be used.
  • the surface of a body 193 of a member in question is provided with grooves 194 forming a heat exchange network.
  • the grooved surface is covered by a thin plate 195, which may be fastened here and there by screws or by welding. If the pressure in the temperature control circuit is kept somewhat lower than that of the working gas, a compression against the body results, even though applied to the rotating member.
  • a straight labyrinth seal may be arranged by using numerous grooves at least in another surface forming the clearance in question.
  • the grooves are transversal in relation to the direction of gas leak and they may be interrupted here and there in cases where there is a possibility for leak also in the direction of the grooves.
  • the circum surface of the working member may be provided with a seal structure 104 extending through the separating wall 21 and thus surrounding the process space, as described in Fig. 4.
  • a seal structure at the bottom of the working space and at the inner surface of the stationary body of the machine.
  • a gas leak takes place in the direction of the movement of the partition wall in relation to the working space and correspondigly in the direction of the movement of the separating wall 21 in relation to the stationary body.
  • the effective speed is now a difference between the gas speed and the speed of the wall in question both taken in relation to the seal structure.
  • Figs. 2-3 are indicating other surfaces to be provided with a straight labyrinth seal, namely in the stationary body of the machine the surface 105 opposite to the end surface 10 of the reacting member as well as surfaces 106 and 107 surrounding the valve openings 26.
  • a labyrinth seal is used in connection with pressure compensations, as indicated in Fig. 9 as to the compensation with the reacting member.
  • the grooves may be partly arranged at the bottom of the mounting piece 34 presented in Fig. 7.
  • the profile of a labyrinth seal may be e.g. that presented in Fig. 47.
  • the profile is formed by grooves 62 be ween ridges 196.
  • a heat exchange of working gas with inner surfaces of the machine may be reduced by using an internal heat insulation.
  • Surfaces into which it is easy to arrange an insulation layer, include stationary surfaces of the valve spaces, side surfaces of the valves, stationary surfaces surrounding the reacting member, the circum surface of the reacting member as well as the bottom surface of the working space in the position of the end portion 22.
  • the surfaces mentioned are characterized in that no precise dimensioning is required.
  • the temperature of working gas near the surfaces remains unchanged during each process cycle.
  • the surfaces mentioned may be shielded in accordance with Fig. 49 with an insulation layer 198 between a base structure 197 and a covering metal plate 199, which may settle down to a temperature near that of working gas.
  • the heat insulation layer may be composed of some sheets 200 in series.
  • the said sheets may be separated from each other by supports 201 of wire type. Supports next to each other may go crosswise whence the structure may bear pressing forces of some magnitude.
  • a pressure level in the insulation space may be maintained as the same as the pressure of the working gas or somewhat smaller. In the latter case the structure may be used also at surfaces of rotating members, because the centrifugal force is overcome by the pressure difference. Because the insulation layer is thin, only a small pressure difference is needed.
  • a suitable pressure level may be arranged by connecting the insulation spaces into a temperature control circuit of the member in question.
  • a possibility for thermal expansion or contraction of the covering plate 199 may be arranged by using foldings 202 in both directions at suitable intervals.
  • a basic fastening into the base structure may be secured by fastening elements 203.
  • the effeciency of the insulation structure presented in Fig. 49 may be based on several surfaces in series.
  • the lack of forced convection would result in a poor heat exchange coefficient at each surface and thus in a sufficient insulation.
  • sheets in series would serve as a shield against radiant losses.
  • T w temperature of wall
  • T 2 temperature of gas after expansion
  • T 1 temperature of gas before expansion
  • p 1 gas pressure before expansion
  • p 2 gas pressure after expansion
  • R universal gas constant
  • c p heat capacity of working gas in constant pressure
  • h heat exchange coefficient
  • a w area of heat exchange surface
  • t time of process cycle.
  • a reducing coefficient 0.25 is used for a part exceeding temperature T 2 , because a higher temperature occurs only for a part of time.
  • Density ⁇ is calculated at the mean temperature of the boundary layer. Heat loss is compared with the work done by gas during one process cycle, namely
  • V 1 0.1D 3 is the maximum volume of one process space before expansion.
  • D 0.75 m
  • the walls may be even near the ambient temperature without resulting in a great relative heat loss. Neither is the heat flow density too great as far as thermal stresses are concerned, if a cooling circulation is arranged near the surfaces in question. Consequently, in connection with the invented machine even very high gas temperatures may be used and still essential parts of the machine be maintained at moderate temperatures. It may be concluded from the formulae presented that the significance of working gas as well as the size of the machine to the relative heat loss is of minor importance.
  • Figs. 50-51 present a heat insulation structure which may be used even to shield surfaces surrounding the process space. If the shield were used at least to a remarkable portion of said surfaces, the heat loss would then be reduced correspondigly.
  • the most suitable surfaces appear to be the stationary surfaces of the body, especially the cylinderic portion, and the bottom portion of the surface in the working member.
  • the surface in question would be covered by plates. 204, which are fastened into a base structure 197 centrally so that thermal expansion or contraction takes place symmetrically in all directions, the middle line 0 of each plate remaining fixed.
  • the plates 204 are supported by a series of co-axial cyliners 205 made of thin material.
  • Said cylinders are installed into corresponding grooves 206 and 207 in the base structure and the covering plate.
  • the idea involved is that a cylinder-symmetrical structure with thin walls may undergo a thermal expansion or contraction due to a temperature gradient in the direction of the central line 0 without excessive thermal stresses in the material being induced.
  • the plates 204 are warmed or cooled isothermally and a temperature change appears at the supports 205, which thus becomes somewhat conical.
  • the use of cyliner-symmetrical supporting structures would result in an essentially greater rigidness against force components transversal to the line 0 than the use of many separate thin supports.
  • the supports 205 may be fastened into the base structure 197 e.g. by welding.
  • fastening to the plates may be done by welding at the position of projection portions 208 extending through the plate in holes made therein.
  • the structure may resist also pulling stresses and is thus suitable to be used in rotating members.
  • the fastening of the plates into the base structure may be effected by using bolts, which would preferably be in thermal contact with the supports 205.
  • the pressure in the underlying space 211 were the minimum pressure of working gas, and if the pressure range used v/ould be as high as 100bar - 50bar,
  • the supports were of iron material with a thermal conduc tivity of 50W/moC, the free hight of the supports were 2 cm and the temperature difference 400oC, then a mean heat flow density of 100kW/m 2 would result. As compared with the table presented above, this would correspond to a relative loss of 1%.
  • a sufficient seal between the process space and the underlying space 211 may be arranged by using a seal 209 with a round cross-section permitting a slight movement in direction of a thermal expansion or contraction.
  • the plates When used in a machine using hot working gas the plates can be dimensioned so that at a high running temperature the slots between the plates are reduced to zero. In a machine using cold working gas this is not possible. In that case an arrangement described in Fig. 52 is possible for preventing gas leak through remaining slots 213.
  • the example is thought to refer to the covering of the surface of the working member.
  • those sides of the plate not parallel to said edge are formed to be of zik-zak character having portions 212 and 213.
  • the slot 212 does not change during cooling of the plates, whereas the slot 213 grows. Because the slots 213 are so short that they do not extend over the edge 45, a continuous gas leak is prevented. The gas volume involved with the slots remains negligible as compared with the volume of the working space.
  • the surface of the plates may be provided with a labyrinth seal structure 210, as sketched in Fig. 51.
  • Fig. 53 an alternative total construction of the machine is sketched.
  • the body 4 of the machine is of one piece, whereas one machine unit consists of two working members 1a and 1b mounted on a uniform power shaft 2. End walls 214 mounted after the working members increase the rigidness of the body.
  • Fig. 54 presents graphically various quantities associated with the machine in accordance with Figs 2-3 as a function of rotation angle ⁇ w of the working member, the origin of ⁇ w -axis corresponding to the situation, where the extreme end of the process space is at the position of the partition wall, corresponding to the starting moment of an expansion cycle. Curves presented include a time course of the total area A of the valve opening as well as the area Apr of the partition wall reduced to a distance D/2
  • the calculation presented may roughly indicate pressure losses in the machine, because the working space corresponds to quite a short and wide flow conduit with low friction losses, taking also into account that one side wall is stationary and the other is moving in the direction of gas flow and that a typical circumferential speed of the centre of gravity of the partition wall is about 0.8v R .
  • all kinetic energy calculated above does not necessarily mean loss.
  • Fig. 54 it is still presented a course of torque M, as it is supposed that two functional basic units are used in opposite phases in accordance with Fig. 1. Fluctuations in the torque curve are of so high frequency that the inertia of rotating masses is sufficient to maintain the speed of rotation practically constant even at high pressures.
  • the structure of the invented machine makes it possible to regulate at least to some extent the pressure ratio by altering the phase angle of the rotation of valves. Then it would be advantageous to have an additional width in the separating wall 21 so that opening of each virtual valve in expansion use and correspondingly closing in compression use would happen totally in the shield of said separating wall within the whole regulating range.
  • Fig. 55 is presenting a total block diagram including main parts of the invented machine as well as external devices needed for accomplishing control functions presented earlier.
  • External devices include a synchronization control unit 236 for synchronization of the other members with the rotation of the working member.
  • a synchronization sensor circuit 215 may utilize some conventional method, e.g. an optical one.
  • Figs. 35-43 are presenting one way as to the reacting member. Precision requirements are considerably lower in the case of the valve members as well as pressure compensators.
  • a temperature control unit 216 regulates mass flow through pumps 186 on the basis of temperature measurements with temperature sensor circuits 217. The pressure level in each thermostat circuit is maintained suitable by means of compressors 218.
  • the diagram includes chambers 219-221 for high pressure gas to be supplied to the sealing members in the reacting members and to pressure compensators presented in Figs. 11 and 14. Pressures needed are produced by compressors 222-224. Conduits for p, and p min may be connected directly to the conduit 19, if the temperature of the working gas is near the ambient temperature. In the case of an expansion machine of a heat power process, a connection may be made into the corresponding conduit 19 of the compressor of the Brayton-cycle. Also is presented means for controlling pressures in the conduits 18 and 19 when a closed process is used.
  • Said means consists of chambers 225-228, valves 229-232, a control unit 233 for regulating said valves so that, when needed, either more gas is entering the process circuit from high pressure chambers 225-226 or part of the gas is removed from the process circuit into low pressure chambers 227-228.
  • Compressors 234-235 are pumping gas from low pressure chambers back into the corresponding high pressure chamber.
  • Figs. 1-55 The presentation of the embodiment according to Figs. 1-55 is so detailed that a person skilled in the art can understand as well as accomplish the invented machine. Auxiliary devices presented in Fig. 55 are conventional. As to the two alternatives concerning the sealing member, a selection between them depends on the application in question. If an emphasis is put on structural simplicity and if disturbances caused by a machine connected to the invented machine are small, the former alternative presented in Figs. 23-24 is adequate.
  • Figs. 56-57 illustrate another kind of modification of the invented machine. By this modification it can be achieved in principle an arbitrarily great pressure ratio, which in addition may be regulative.
  • Fig. 56 presents the machine at the section corresponding to Fig. 3, whereas Fig. 57 corresponds to Fig. 4.
  • the rotation space of the working member includes an extension part 48 surrounding the cylindrical main part, the separating wall 21 of the working member being provided with a projection part 50 corresponding to the cross-section of the channel 48 in the body of the machine.
  • the partition wall forming part 10 is provided with one transition sector 77.
  • the edge line of the partition wall forming part 10 is now of such general form that when the angle co-ordinate ⁇ r varies starting from the sector, which is turned towards the working member when process cycle changes and the separating wall 21 between working spaces 5 is correspondingly turned towards the reacting member, to a direction corresponding to the order of arrival of various points of said edge line in expansion use into the rotation space of the working member, the radial co-ordinate increaces from the minimum value r 0 at first to an intermediate value r 1a , v/hence the reacting member is extending into the mentioned projection part 48, but not yet into the main part of the rotation space of the working member, and in the second phase to the maximum value r 1b , whence the reacting member now extends also into the main part of the rotation space, and at last said co-ordinate decreases to the starting value r 0 near the completion of the whole circle.
  • the form of the working space corresponds to said form of the reacting member.
  • a process phase corresponding to an open valve is restricted to the projection part 48 resulting in a small cross-section of the partition wall, whereas during the process phase corresponding to the closed valve also the main part of the rotation space is in use, resulting in a great cross-section area of the corresponding partition wall. Consequently, a great volume ratio can be achieved.
  • the valve of the machine may be of the same kind as was presented in connection with the preferred embodiment of the invention. Because the cross-section area of the projection part is small, it is possible to manage with one true valve member, by means of which three virtual openings may be formed as presented earlier. If the projection part 48 is located symmetrically in relation to the reacting member, it is possible to interconnect the shafts of said members by means of a universal joint, whence the rotation of the valve member may happen through the reacting member.
  • Figs. 58-59 illustrate still another modification of the invented machine. In this modification no true valves are needed.
  • Fig. 58 is corresponding to Fig. 3 and Fig. 59 to Fig. 4.
  • the partition wall forming part 10 has one transition sector 77.
  • the edge line of the partition wall forming part 10 of the reacting member has now such general form that as the angle co-ordinate ⁇ r is varying starting from the sector, which is turned towards the working member, when the process cycle changes and the separating wall 21 between working spaces 5 is turned correspondingly, towards the reacting member, to a direction corresponding to the order of arrival of various points of said edge line in expansion use into the rotation space of the working member, the radial co-ordinate is increasing from the minimum value r 0 to the maximum value r 1 , decreasing after this to an intermediate value r 2 , and finally to the starting value r 0 near the completion of the whole circle.
  • the 59 is presenting the form of the working space 5 as a function of the rotation angle ⁇ w of the working member and of the co-ordinate z in the direction of the rotation axis of the working member. It is characteristic of the working space that a section 237 at the process space end, corresponding to the maximum radius r 1 of the reacting member, is extending further sidewise in direction of the rotation axis of the working member than any other part of the working space. Then the gas opening 26 may be located in the body of the machine so that in direction of the circumference of the working member it is located on the process space side of the partition wall 15 and extends close by said wall so far in direction of the rotation axis of the working member that only the mentioned section 237 extends to the position of said opening.
  • the valve operation may be based on the rotation of the working member.
  • the opening 26 is closed by the unbroken part 238 of the circum surface of the working member.
  • the valve starts to open, when the process space end of the working space and thus also the section 237 is passing the position of the partition wall 15, and the valve is closing as the section 237 has proceeded over the opening 26.
  • Fig. 60 illustrates a possibility to combine two functional units 40 in parallel so that reacting forces induced are compensating each other. It would be easiest to utilize this possibility in connection with the embodiment in accordance with Figs. 58-59, because then the valves are not in the way.
  • By using a force pair F-F it would be possible to arrange a compensating moment whence a bending moment to the shaft 9 can be avoided.
  • each real expansion machine is replaced by a substitute model in accordance with Fig. 62, and correspondingly the compressors are replaced by a substitute model in accordance with Fig. 63.
  • the substitute models have an ideal expansion or compression machine M e or M c with a parallel block 239 denoting relative gas leak a, and a serial block 240 denoting relative pressure change b especially in the valve opening. If the pressure ratio in the real expansion machine is p 3 /p 4 , appears the pressure ratio (1-b)p 3 /p 4 over the ideal expansion machine, resulting in a temperature fall of working gas
  • e (T 2 -T 1 ) / (T 4 -T 1 ) is the temperature effeciency of the heat exchanger E
  • coefficient m. is taking into account heat losses into walls of hot spaces.
  • waste heat flow Q out can be removed from the process in a profitable form from the secondary side E ls of the counter-current heat exchanger E 1 . If the pressure ratio in the machines of the process were of the order 1.8:1, a rise of temperature in the compressor and also on the secondary side of the heat exchanger would be of the order of 80°C . By selecting the pressure ratio properly the process may be planned for various uses of waste heat.
  • Each expansion and compression machine has been thought to comprise two functional units in accordance with Fig. 1.
  • the maximum temperature of working gas is supposed to be about 800K (about 530oC). If air were used as working gas instead of helium, power attainable would be about half of that indicated in the table due to a lower speed of rotation.
  • Most of weight is in the stationary body of the machine, which may be lightened somewhat e.g. by radially extending cavities, whence individual material thicknesses are not so great thinking about manufacturing e.g. by using casting technique. If the body is composed of several parts by using welding technique, possibilities for a considerable lightening are good.
  • weights of heat exchangers needed in the Brayton-process are only of moderate order, when a closed high pressure process is used, especially with a light-weighted working gas.
  • heat exchangers are needed also in a Rankine-cycle.
  • Weights of non-condensing turbines may be of the order of 1 kg/kW, but the effeciency as to mechanical or electric energy is essentially lower.
  • One interesting reference would be slowly running dieselengines, e.g. in large ships or for a power plant use, which may have a weight of 40 kg/kW, for example.
  • drawbacks include that only expensive oil can be utilized as energy source and that life time is not the best possible.
  • Figs. 65-66 present process diagrams of the energy storing process especially when a solid cold store is used, Fig. 65 corresponding to a charging period and Fig. 66 to a discharging period.
  • the process cycle 251 is a Brayton-cycle provided with a heat exchanger E between warm and cold parts of the circuit.
  • the cycle includes a machine M h working near or above the ambient temperature and a machine M 1 working below the ambient temperature.
  • the machine M h functions as a compressor, whereas the machine M 1 operating on a lower temperature level funtions as an expansion machine. Consequently, mechanical work must be fed to the process during the charging period.
  • the working gas is warmed in the compressor M, from temperature T 4 ' to temperature T 3 '.
  • the gas is cooled in a counter-current heat exchanger E h to temperature T 2 ', in other words approximately to the temperature before compression.
  • Water taken from a cold water store S s or from an open water supply is circulated by means of a pump P h in the circuit 253 so that the temperature of the water rises in the heat exchanger E h e.g. to 90-100oC, whereafter the water is stored in a hot water store S h .
  • the working gas is further cooled in the heat exchanger E r to temperature T 1 ' and after that in the expansion machine M 1 to temperature T 0 '.
  • the gas is then warmed up in the counter-current heat exchanger E to temperature T 5 ', thus making it possible to remove heat from the cold store S 1 .
  • the working gas is heated in the heat exchanger E to the temperature T 4 ' mentioned earlier, at which the process cycle has become completed.
  • the maximum temperature T 3 ' of the gas may naturally be permitted to exceed +100oC by an amount corresponding to a temperature difference needed in the heat exchanger E h . Additionally, the minimum temperature of water may be even under 0oC, if salty water is used.
  • the cold store circuit 252 some fluid, e.g. air is circulated with the aid of pump means P 1 .
  • the cold store S 1 being of solid material it may be provided with a multiplicity of parallel flow conduits, so that the store may be used as a regenerator having a very great time constant.
  • the temperature of the cold store decreases slowly.
  • a temperature gradient is permitted to be created in the storing material in the direction of conduits so that the temperature difference between the ends of the store is of the same order as the change of gas temperature in the machine M 1 working at a lower temperature level.
  • the process is used in the opposite direction. Then the machine M h working at a higher temperature level is used as an expansion machine, whereas the machine M 1 working at a lower level is used as a compressor. Consequently, the process is capable of producing mechanical work. From the store S h is taken hot water, which is cooled down in the process before going into the cold water store S s or to the open surroundings. As working gas is cooled in the heat exchanger E 1 from temperature T 5 to temp rature T 0 , the corresponding heat amount is got into the cold store S 1 , the temperature of which thus slowly rises.
  • the process may include both on the warm and cold sides several machine heat exchanger pairs (M h -E h , M 1 -E 1 ) in series, resulting in smaller losses caused by the heat exchanger E r having a certain temperature efficiency.
  • the process diagram presented may be modified so that the cold stores is directly a part of the circuit 251, whereby working gas would circulate through the cold store, the heat exchanger E 1 as well as the pump means P 1 being omitted.
  • an additional liquid-form circuit between the cold store S 1 and the process circuit 251 may be used for transmitting the cold capacity over a considerable distance.
  • the change of water temperature in the storing process may be of the order of 40-100oC, whereby the corresponding change of gas temperature in the cold machine M 1 may be 10-60oC, depending partly on the temperature level at which the cold machine functions at each moment.
  • Figs. 67-68 present partial process diagrams for a charging period, when liquid material is used in the cold store. If the material is in a liquid form over a wide temperature range, e.g. between -40oC - -180°C, the whole range may not be utilized in one process stage. Then it is possible to use arrangements according to Figs. 67-68. In the both cases two cold store units are used, the store unit S la containing colder liquid and the unit S lb warmer liquid. In Fig.
  • the temperature of liquid in the store S lb is at an upper limit of the temperature range used and during a charging period liquid taken from the said store unit is circulated by the pump P 1 through several heat exchangers E 1 , the cold store sides of which are connected in series and being thus cooled down to the lower limit of the total temperature range used before transferring into the store unit S la , which thus receives liquid having a minimum temperature.
  • the opposite sides E 1p of corresponding heat exchangers are each connected to corresponding process cycles, which are in parallel, but the lower temperatures of which are stepped so that temperature ranges in cold machines of the various circuits together cover the temperature range used for cold liquid.
  • the parallel circuits mentioned may be wholly separate, or they may have the machine M h and the heat exchanger E h in common.
  • Fig. 68 only one process cycle is needed.
  • Cold liquid is transferred by the pump P 1 during charging period from a warmer store unit into a colder one, until the first-mentioned store is empty.
  • the direction of circulation is reversed by using valve means V 1 and V 2 so that liquid is transferred from the full store into the empty one and is still cooled because direction of circulation remains unchanged regarding the heat exchanger E 1 .
  • the working temperatur level of the cold machine M 1 is lowered. The described manner of proceeding may be repeated until the whole tempe- rature range has been utilized.
  • the cold store side of the process may be also based on liquefying of air. Because air cannot be stored in a gas form in great quantities, during the charging period air taken from the atmosphere must be cooled at least to the boiling point of air in addition to liquefying. Then the process machinery needed may be more complicated than in the case of a store having material continuously in a solid or liquid form. On the other hand, specific capacity is increased if also the capacity involved in cooling and heating of air is utilized.
  • One difficulty associating with the use of air is that the invented machine fits well with a Brayton-cycle having isentropic work phases, whereas in utilizing heat involved in liquefying and boiling, isothermal work phases would be natural for achieving a reversible process. In the process diagram presented in Fig.
  • the boiling points of oxygen and nitrogen in air are quite near each other, whence boiling of air takes place within quite a narrow temperature range, which as a rough approximation can be called the boiling point of air in the total pressure in question.
  • the temperature of air at each joining point i 1 -i n of the corresponding flow conduit C 1 -C n to the heat exchanger E 1 is arranged to correspond to the boiling point or. strictly speaking to the upper limitation of the boiling range at the pressure in question.
  • combinations of pressure and temperature corresponding to the vapour pressure curve are arranged in the following way.
  • Adapting of pressure is accomplished so that in each flow branch C 1 -C n-1 expansion machines are used M r1 -M r (n-1) having an individual pressure ratio selected to result in the wanted pressure after expansion.
  • Adapting of temperature as a correct one is accomplished so that air passes through the heat exchanger E r ' l , which is cooling air during the charging period.
  • the air side of said exchanger is provided with joining points j 1 -j n for parallel air conduits C 1 -C n , the joining points being situated so that the temperature of air at each joining point is suitable for the conduit in question.
  • the input point 256 of air leads to a chain of machines M 1 -M k functioning as compressors for compressing air into a high pressure.
  • the chain includes heat exchangers E 1 -E k for cooling air warmed up to about 100oC back near the temperature of cold water.
  • water going into the warm water store S can be heated.
  • isobaric cooling of air in said heat exchangers the moisture of air is condensed and can be separated.
  • the high pressure air during charging period goes into the expansion machine M r0 , in which air is cooled considerably due to expansion, e.g. to a temperature of the order of 150K (about -120°C), after which the air goes to the input j 0 of the heat exchanger E r ' l .
  • Each working gas circuit E l ' 1 -E l ' n functions as a cold side heat exchanger of a Brayton-cycle with a corresponding cold machine M l ' 1 -M l ' n .
  • the temperature change on the air side of E' within the section E r ' 1 adjacent to the machine M r0 may be of the order of 10-20oC, whence a moderately great temperature variation results in the first cold machine M l ' 1 .
  • temperature ranges may be small, the size of the temperature range growing gradually from one cold machine to another. If the number of parallel branches
  • C 1 -C n is very great, it is possible without essential losses to use a more rough division on the v/orking gas side so that one working gas circuit corresponds to two or several branches for air flow.
  • Branches consisting of heat exchange circuits E l ' 1 -E l ' n and cold machines M l ' 1 -M l ' n can be joined to form cold side circuits of parallel Brayton-cycles having approximately the same pressure ratio, so that the sum of temperature ranges of cold machines in each process is approximately the same, and the total pressure ratio is divided on the warm side of the process over several compression machines in series so that the temperature rise of working gas during charging period is suitable for warming up water going into the warm store S h .
  • hot water going into the warm store may be produced in three parallel circuits, namely in the phase change circuit 251, in the temperature change circuit 254 and in the pressure change circuit 255.
  • the two circuits mentioned first are closed Brayton-cycle circuits, in which helium or hydrogen may be used as working gas.
  • the third circuit is an open air circuit, which includes machines M 1 -M k working above or near the ambient temperature as well as machines M r0 -M r(n-1) working under the ambient temperature.
  • the process is run in an opposite direction. Liquid air is then taken from the cold store S 1 , and gaseous air is released into the atmosphere from the point 256. Hot water taken from the the warm store
  • the temperature at the low temperature end of E r would be about 100K (-170°C) or more, whence in case of helium as a working gas the pressure dependancy of the specific heat of the working gas would yet be so small that conditions for a theoretically ideal heat exchanger E r between the warm and cold sides of the Brayton-cycle still exist.
  • the process diagram presented may be modified e.g. so that the temperature range of the heat exchanger E 1 is shifted to a higher temperature level, e.g. within a range
  • Fig. 70 presents a partial process diagram relating to that presented in Fig. 69.
  • the modification of Fig. 70 aims at simplifying the temperature change circuit 254 of Fig. 69.
  • Suitable combinations of pressure and temperature for parallel flow conduits C 1 -C n of the heat exchanger E l are achieved by permitting, during the charging period, a small fraction of cooling air liquefy in some expansion machines M r1 -M r ( n- 1 ) , whence an amount of heat needed for keeping the temperature of air at the boiling point at the pressure in question is released.
  • a numerical value n 10 has been presumed, whence machines M r1 -M r9 are needed. Said machines are divided into four groups, each of which includes 1-3 machines.
  • Each substitute model includes an ideal machine M h , or M l , a parallel block 239 denoting relative gas leak a and a serial block 249 denoting relative pressure change b especially in the valve opening.
  • the temperature fall of the working gas in the ideal expansion machine may be expressed by the equation
  • the temperature rise of working gas in the ideal compression machine may be expressed in the form
  • Fig. 73 presents graphically the calculated efficiencym as a function of the minimum temperature T 0 ' of working gas in the charging process at some values of loss parameters a, b and c.
  • the efficiency of 50% may already be considred quite satisfactory, because part of the energy may be transmitted directly to consumers without storing.
  • the characteristic of the invented storing process is that the part of stored energy, which is not reversible to mechanical energy, remains in form of heat in the hot water store and, thus, in a form profitable for low temperature purposes.
  • the best efficiency may be achieved in short-term storage and by using liquid as a cold store material. Then temperature differences T 3 '-T 3 and T 0 -T 0 ' would be at the minimum as well as thermal leakage into the cold store.
  • the equation derived may also be applied to circuits 251 and 254 in Figs. 69-70.
  • the efficiency of the circuit 255, in which the store air is directly flowing, is expected to be high.
  • the efficiency of the process may be altered in some extent by using different pressure ratios during charging and discharging periods.
  • a moderate control range of pressure ratio is easy to arrange in the invented machine.
  • the total range of the temporal temperature variation may be about 70-80oC without the mean efficiency being remarkably lower than the maximum one. Then if a solid store were used, the temperature range of the colder end of the store might be within 100K-180K (about -170°C - -90°C), for example.
  • the store temperatures would be approximately within 100K - 230K (about -170°C - -40°C), in which both temporal and local variations have been taken into account.
  • Fig. 73 reveals, how strongly the efficiency of the storing process is decreased by losses of machines. Thus, it is clear that turbo-machines are not competitive in this application, neither other known machines.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)

Abstract

Une machine du type a deplacement positif pour la detente ou la compression de fluides compressibles, dans laquelle le couple cree ou applique exerce un effet direct sur l'arbre de transmission, les paliers de l'arbre ne sont charges que par les poids de masses rotatives correspondantes, la lubrification etanche n'est pas utilisee, et la structure devrait faciliter l'obtention de faibles pertes. La machine comprend des volumes de travail (5) delimites par un element rotatif (61) et un corps (4), animes d'un mouvement circonferentiel en meme temps que l'element (1), leur direction principale coincidant avec ladite direction circonferentielle. Les volumes de travail (5) sont subdivises en un espace de traitement (6) et un espace de transfert (7) separes par une paroi (15) qui fait partie d'elements rotatifs de reaction (8) perpendiculaires a l'element de travail synchronises avec celui-ci, et dont la solidite est telle qu'elle leur permet de transmettre a l'exterieur de l'element de travail des forces importantes produites par la difference de pression entre lesdits espaces (6, 7). Ces forces peuvent etre compensees par une contre-pression programmee exercee sur une surface (11) de l'element de reaction. Selon le sens de rotation de l'element de travail, le fluide compressible circulant dans la machine est detendu ou comprime. Les vannes rotatives (23) sont utilisees de preference pour assurer une fermeture cyclique de l'espace de traitement (6). La surface instantanee de l'ouverture de vanne peut correspondre sensiblement a la surface instantanee de la paroi de separation (15). La poutre (10) de l'element de reaction formant paroi de separation comprend de preference un seul secteur de transition (77) pour modifier le cycle du procede, et les exigences de synchronisation sont limitees. On utilise de preference des elements d'etancheite (110) legers afin de reduire les effets de pertes provoques par des erreurs de synchronisation. On peut maintenir les fuites qui ne dependent pas de la synchronisation a un faible niveau en controlant la temperature des differentes parties. La plupart des passages formant fuite peuvent etre munis d'un joint d'etancheite (61, 103, 104) reduisant la vitesse du gaz de fuite.
PCT/SE1979/000037 1978-02-22 1979-02-19 Machine de detente ou de compression de gaz ou de vapeurs Ceased WO1979000652A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
JP79500426A JPS56500222A (fr) 1978-02-22 1979-02-19
BR7906804A BR7906804A (pt) 1978-02-22 1979-02-19 Maquina para a expansao ou compressao de gases ou vapores e emprego da maquina para armazenamento de energia

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
FI780584 1978-02-22
FI780584 1978-02-22
FI781910 1978-06-15

Publications (1)

Publication Number Publication Date
WO1979000652A1 true WO1979000652A1 (fr) 1979-09-06

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Application Number Title Priority Date Filing Date
PCT/SE1979/000037 Ceased WO1979000652A1 (fr) 1978-02-22 1979-02-19 Machine de detente ou de compression de gaz ou de vapeurs

Country Status (6)

Country Link
EP (1) EP0009047A1 (fr)
JP (1) JPS56500222A (fr)
AU (1) AU537777B2 (fr)
BR (1) BR7906804A (fr)
CA (1) CA1152468A (fr)
WO (1) WO1979000652A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101198032B1 (ko) 2011-03-08 2012-11-06 비아이피 주식회사 유체의 팽창을 이용한 발전 시스템

Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US928506A (en) * 1908-06-26 1909-07-20 Louis Labadie Driggs Rotary engine.
US990665A (en) * 1910-04-05 1911-04-25 John Norin Rotary engine.
FR563981A (fr) * 1923-03-07 1923-12-18 Moteur rotatif à explosions
DE449553C (de) * 1925-11-14 1927-09-16 Richard M Hofmann Verbrennungskraftmaschine mit umlaufenden Kolben
FR908371A (fr) * 1944-06-06 1946-04-08 Machine rotative
GB937265A (en) * 1960-02-24 1963-09-18 John Paine Renshaw Improvements in rotary motors and pumps
GB1009066A (en) * 1962-12-31 1965-11-03 William Biswell Mccall Rotary internal combustion engine
CH433861A (de) * 1965-07-14 1967-04-15 Schlupo Gottfried Drehkolbenmaschine
US3514239A (en) * 1968-06-20 1970-05-26 K M F Dev Corp Modular housing for rotary engine
SE336190B (fr) * 1969-06-18 1971-06-28 Atlas Copco Ab
DE2104595A1 (de) * 1971-02-01 1972-08-10 Nadolny, Gerhard, 4630 Bochum Drehkolbenmaschine
DE2516177B2 (de) * 1974-04-15 1978-05-24 Hokuetsu Kogyo Co. Ltd., Niigata (Japan) Geschränktachsige Rotationskolbenmaschine

Patent Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US928506A (en) * 1908-06-26 1909-07-20 Louis Labadie Driggs Rotary engine.
US990665A (en) * 1910-04-05 1911-04-25 John Norin Rotary engine.
FR563981A (fr) * 1923-03-07 1923-12-18 Moteur rotatif à explosions
DE449553C (de) * 1925-11-14 1927-09-16 Richard M Hofmann Verbrennungskraftmaschine mit umlaufenden Kolben
FR908371A (fr) * 1944-06-06 1946-04-08 Machine rotative
GB937265A (en) * 1960-02-24 1963-09-18 John Paine Renshaw Improvements in rotary motors and pumps
GB1009066A (en) * 1962-12-31 1965-11-03 William Biswell Mccall Rotary internal combustion engine
CH433861A (de) * 1965-07-14 1967-04-15 Schlupo Gottfried Drehkolbenmaschine
US3514239A (en) * 1968-06-20 1970-05-26 K M F Dev Corp Modular housing for rotary engine
SE336190B (fr) * 1969-06-18 1971-06-28 Atlas Copco Ab
DE2104595A1 (de) * 1971-02-01 1972-08-10 Nadolny, Gerhard, 4630 Bochum Drehkolbenmaschine
DE2516177B2 (de) * 1974-04-15 1978-05-24 Hokuetsu Kogyo Co. Ltd., Niigata (Japan) Geschränktachsige Rotationskolbenmaschine

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101198032B1 (ko) 2011-03-08 2012-11-06 비아이피 주식회사 유체의 팽창을 이용한 발전 시스템

Also Published As

Publication number Publication date
JPS56500222A (fr) 1981-02-26
EP0009047A1 (fr) 1980-04-02
CA1152468A (fr) 1983-08-23
BR7906804A (pt) 1980-02-26
AU537777B2 (en) 1984-07-12
AU4434379A (en) 1979-08-30

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