PAIR OF INTERACTING GEAR RIMS OF THE ROTARY MACHINE

Abstract: A pair of interacting gear rims of rotary machine has been invented as a basis structural element for engines, motors and compressors. This is the most simple and most effective design to predetermine the optimal ratio of volumes of expansion and compression processes only at the expense of the form of profile of contact surface of pair gear rims of the rotary machine. This is the ideal basic element for engines, working according to an extended indicator diagram, and for single stage compressor, working with multistage effect. Applications: light and heavy vehicle engines; space power systems; heat pump systems; solar, thermal, nuclear energy systems.

Description: PAIR OF INTERACTING GEAR RIMS OF THE ROTARY MACHINE BACKGROUND - FIELD OF INVENTION The invention concerns pair of gear rims - basic part of a design of rotary machines, in which the working process is carried out in chambers of variable volume formed as a result of interaction of pair eccentrically located gear rims, and can be used as in rotary machines with one rotor eccentrically located in static stator, and in rotary machines with several, in particular, with two, eccentrically located rotors. Declared pairs of gear rims can be used as a basic element of engines, pumps, compressors, hydro- and pneumatic motors, turbocompressors and other types of rotary machines. BACKGROUND - DESCRIPTION OF PRIOR ART The existing rotary machines are characterized in cumulative volume of process of compression and cumulative volume of process of expansion at rotation of system of rotors at 360° (further for brevity - volume of compression and volume of expansion). The known rotary machines are characterized by equality of volume of compression and volume of expansion at rotation of rotors at 360°. Thus if only one of these processes is used - ether only compression or only expansion, only one these volumes is useful. Thus volume of used process is equal to volume of process, unused in the machine. It is a deficiency of rotary machines of such type. In some cases, while using in the machine both processes, the excess of volume of expansion above volume of compression is energetically favorable. So, for example, in order to use it as the engine, volume of expansion should be more than volume of compression (Kristiansen's cycle). It well known, accepted as the prototype, rotary machine by Galloway, dated 1846, (" Rotary Piston Machipes ", Author F. Wankel, Published by London life Books Limited.), in which the Working chambers are formed between interacting contact surfaces of pair of gear rims located on an inner surface of outer rotor and an outer surface of inner rotor respectively. The rotors are located with eccentricity equal to a difference of radiuses of interacting subsurfaces of gear rims on outer and inner rotors respectively. The profile of contact surface of inner and outer gear rims has an axis of symmetry, bounded by conjugated arcs and represents the closed smooth curve consisting of n>2 identical parts, conjugated among themselves. The identical part of contact surface of a gear rim is bounded by two conjugated arcs of a circle. That provides equal maximal volumes of expansion and compression chambers. The rotary machine by Galloway is one of the simplest constructions of rotary machines with two eccentrically located rotors, it has the above mentioned deficiency of equally used and unused volumes of the machine. There are a lot of known gear rim rotor designs of rotor machines, with eccentrically located rotors one inside the other with eccentricity equal to the difference of the interacting surface radiuses of gear rims of the outer and inner rotors respectively. In these rotors the profile of contact surface of a gear rim represents a closed curve, determined by those or other geometrical figures. The interaction of contact surfaces of gear rims located on outer and inner rotors, results in a formation of variable volume chambers - compression and expansion chambers, in which there are above mentioned processes, volumes of which, are as described above, equal among themselves, and have a common deficiency. There is a known number of the patents: US4932850, US5066207, US5658138, US5720251. All designs under the specified patents are characterized by different rotors of the complex form made of set of elements of various geometry, that is an additional deficiency of the machine. There is a known number of engines under the patents US5433179 and USRE30565, where for altering a ratio of compression and the expansion volumes complex constructive solutions are offered, that considerably reduce reliability of the machine. SUMMARY The invention, briefly, concerns a profile of contact surface of a gear rim of a rotor and/or stator of a rotary machine, having no less than one pair of gear rims - inner and outer, interacting with each other with creation of variable volume chambers, eccentrically located one inside the other with eccentricity e equal to the difference of the interacting surface radiuses. The claimed machine can have one pair of gear rims, interacting with each other with creation of variable volume chambers or several such pairs. The profile of contact surface of inner and outer gear rim has an axis of symmetry, bounded by conjugated arcs and represents closed smooth curve, consisting of n>2 identical parts, conjugated among themselves. Identical part of the inner gear rim is bounded by the arc of radius p- j , conjugated at its ends with the concentric arcs of radius q- j and of radius a+p- j , where a = p- j + q- j . Arc of radius q^ conjugated at the other end with the arc of radius b +q - j , where length b >0. Arc of radius b +q- j is conjugated at the other end with the arc of radius a + p- j of adjacent identical part, which completes the gear rim profile. Identical part of the outer gear rim is bounded by the arc of radius p 2 = p- j + e, conjugated at its ends with the concentric arcs of radius q 2 = a - p 2 and of radius a + p 2 . Arc of radius q 2 conjugated at the other end with the arc of radius b +q 2 , which is conjugated at the other end with the arc of radius a +p 2 of adjacent identical part, which completes the gear rim profile. From the said above it follows, that center of arcs of radius p- j and p 2 is arbitrary placed at the distance a>0 from the center of arcs of radiuses q- j , a+p- j , q 2 , a+p 2 . The center of arcs of radiuses b+q- j M b+q 2 is placed at the distances b>0 and b+2a from the center of arcs of radiuses q- j , a+p- j , q 2 , a+p 2 given and adjacent identical parts. Partition of the working surface profile into identical elements is a particular way of describing the profile. This invention defends the form of the profile of the rotor, bounded by conjugated arcs in a given order independently from grouping identical elements and without it. The invention defends the profile of contact surface of a gear rim of the rotary machine, which provides for the creation of two types of chambers of variable volume. Achieving - more than a double distinction between volumes of processes, carried out in the machine, - expansion and compression, and only at the expense of the profile of contact surface of a gear rim. At the same time, the increase of specific productivity and yield of the rotary machine, both inner and outer gear rims are characterized by a uniform technique of construction, that considerably simplifies design, and manufacturing of rotors. DRAWING FIGURES Fig. 1. Pair of gear rims at n=7. General view. Fig. 2. Construction of an identical part of a profile of contact surface of pair of gear rims; generic case; n=4. Fig. 3. Construction from identical parts of full profile of contact surface of pair of gear rims; generic case; n=4. Fig. 4. Working relative placement of a pair of interconnected gear rims; generic case; n=4. Fig. 5. Construction of an identical part of a profile of contact surface of pair of gear rims in a case with center S j < arcs of radiuses b+q« j M b+q 2 located on the line between centers S^ and Q^ arcs of radiuses q- j , a+p- j , q 2 , a+p 2 ; n=5 and b=a. Fig. 6. Construction from identical parts of full profile of contact surface of pair of gear rims in a case with center S^ located on the line between centers Q | < and S |ς ; n=5 and b=a. Fig. 7. Working relative placement of a pair of interconnected gear rims in a case with center S j < located on the line between centers Q^ and S^ ; n=5 and b=a. Fig. 8. Construction of an identical part of a profile of contact surface of pair of gear rims in a case with center S^ located on the line between centers Q j < and S | < ; n=6 and b=0. Fig. 9. Construction from identical parts of full profile of contact surface of pair of gear rims in a case with center S^ located on the line between centers Q^ and Fig. 10. Working relative placement of a pair of interconnected gear rims in a case with center S^ located on the line between centers Q^ and S^ ; n=6 and b=0 Fig.11 , a-d. Disk version of rotors with two pairs of gear rims. Fig.12-13. A schematic example of possible design of the machine. DETAILED DESCRIPTION OF THE DRAWINGS Fig. 1. General view of the pair of gear rims is given at n=7. Pair of gear rim consists of an inner gear rim 1 and outer gear rim 2. Fig. 2, 5, 8 illustrates identical part k, ke[1,n], of a declared profile of contact surface of both inner and outer gear rims of the rotary machine. Each gear rim contact surface profile is bounded by arcs with center points P^ arcs of radiuses p- j and p 2 , Q^ arcs of radiuses q- j , a+p- j , q 2 , a+p 2 and S^ arcs of radiuses b+q- j H b+q 2 , ke[1,n]. The centers P^ are arbitrary located at distance a from centers Q^ , that is they can be located on circles of radius a with the centers Q k . The location of the centers P^ relative to centers Q^ defines a slope of rim teeth. Center S k is located at a distance b>0 from the center Q^ and at a distance b+2a from the center Qk+1 of adjacent an identical part k+1. When the center S^ is located on a line of the centers P^ and Q k and coincides with the center P k , b=a (fig.5-7), and the distance between centers S k and equals 3a. When the center S k is located on a line of centers P^ and Q^ and coincides with the center Q k , b=0 (fig.8-10), and the distance between centers S^ and Q +1 equals 2a. The concrete location of centers S k relative to centers Q k defines ratio of volumes of expansion and compression processes, which are carried out in the machine. On fig.2-10 the numbering of identical parts of a rim is accepted in a counterclockwise direction, that defines a direction of a slope of gear rim teeth. At change of direction of numbering of identical parts of a rim, the direction of teeth slope of a gear rim will change. Profile of an identical part k of a contact surface of inner gear rim is limited by an arc Ci Bi of a radius p- j with the center Pk .conjugated by one end in a point Ci with an arc Ci Di of a radius q- j = a-p- j with the center in Q and at the other end in a point Bi with an arc Af Bi of a radius a+p- j with the center Qk , concentrical to an arc Ci Di . The arc C-j Di is conjugated in a point Di with an arc Di El of a radius b+q^ with the center S k . From a condition of limitation of a profile of contact surface by conjugated arcs of circles, follows, that adjacent asymmetrical parts of rim profile are conjugated among themselves, that is the arc Di Ei , limiting an identical part k of a profile of contact surface of an inner gear rim, in a point Ei is conjugated to an arc Ai Bi adjacent identical part k+1 of a profile in a point Aι . That is two circles of radiuses b+q- | and a+p- j with centers in S and Qk+1 are conjugated and also two circles of radiuses a+p^ and b+q^ with centers in Qk and Sk.- j are conjugated, where Qk+1 and S^.- j - centers of arcs with radiuses a+p< | and b+q^ of adjacent identical part k+1 and k-1 respectively. Since the conjugation of two arcs occurs in a point on their centerline, the distance between centers Sk and Qk+1 , and also centers Qk and S^.^ is equal (b+q- | )+( a+p^ )= b+2a. Profile of an identical part k of a contact surface of outer gear rim is limited by an arc C2 B2 of a radius p 2 with the center Pk .conjugated by one end in a point C2 with an arc C2 D2 of a radius q 2 = a-p with the center in Qk and at the other end in a point B2 with an arc A2 B2 of a radius a+p 2 with the center Q , concentrical to an arc C2 D2 . The arc C2 D2 is conjugated in a point D2 with an arc D2 E2 of a radius b+q with the center S^ . From a condition of limitation of a profile of contact surface by conjugated arcs of circles, follows, that adjacent asymmetrical parts of rim profile are conjugated among themselves, that is the arc D2 E2 , limiting an identical part k of a profile of contact surface of an outer gear rim, in a point E2 is conjugated to an arc A2 B2 adjacent identical part k+1 of a profile in a point A2 . That is two circles of radiuses b+q 2 and a+p 2 with centers in S^ and Qk+1 are conjugated and also two circles of radiuses a+p and b+q 2 with centers in Qk and S^.- j are conjugated, where Qk+1 and Sk.- j - centers of arcs with radiuses a+p 2 and b+q 2 of adjacent identical part k+1 and k-1 respectively. Since the conjugation of two arcs occurs in a point on their centerline, the distance between centers S^ and Qk+1 , and also centers Qk and S^.^ is equal (b+q 2 )+( a+p 2 )= b+2a. Fig. 3 illustrates the construction from identical parts of a contact surface of pair of gear rims in the generic case while n=4. Pair of profiles has an axis of symmetry of the fourth order C4 . Each contact surface profile of a gear rim consists of four identical parts, conjugated in their boundary points. For illustration purposes, the points of inner and outer rims with identical indexes are connected by segments, dividing pairwise identical parts of a pair of gear rims. The centers of all arcs, that limit profiles of both inner and outer gear rims, for an identical part k are located in points P k ,Q k and S j < e[1,4]. Fig. 6 illustrates the construction from identical parts of a contact surface of a pair of gear rims in the case where centers P k and S^ are superposition while n=5. Pair of profiles has an axis of symmetry of the fifth order C5 . Each contact surface profile of a gear rim consists of five identical parts, conjugated in their boundary points. For illustration purposes, the points of inner and outer rims with identical indexes are connected by segments, dividing pairwise identical parts of a pair of gear rims. The centers of all arcs, that limit profiles of both inner and outer gear rims, for an identical part k are located in points P k ,Q | < and S ke[1,5]. Fig. 9 illustrates the construction from identical parts of a contact surface of a pair of gear rims in the case where centers Q^ and S^ are super positioned (b=0) while n=6. Pair of profiles has an axis of symmetry of the sixth order Cβ . Each contact surface profile of a gear rim consists of six identical parts, conjugated in their boundary points. For illustration purposes, the points of inner and outer rims with identical indexes are connected by segments, dividing pairwise identical parts of a pair of gear rims. The centers of all arcs, that limit profiles of both inner and outer gear rims, for an identical part k are located in points P^ .Q^ and Sk ke[1,6]. Fig. 4,7 and 10 illustrate a working condition of interaction of an inner rim 1 and outer rim 2, which are located with relative eccentricity e = I P2 - P1 I = I qi — 2 I - On both sides of a tooth of the gear rim two types of variable volume chambers are created: A and B. Simply connected region, where gear rims are not interacting, is the chamber of variable volume C. Chambers of the type A or B, in which expansion process takes place, after reaching it's maximal volume, they break up and unite with chamber C. Chambers of the type A or B, in which compression process takes place, are created in their maximal volume as a result of closing portion of space of chamber C. The maximal values of volumes vary. The ratio of this variance, for a concrete working process, is set at the design stage of the machine. So, the maximal volume of chambers of type A and B, on fig.4 have a ratio of distinction 2.65, on fig.7 - 2.08, on fig.10 - 1.86. On fig. 4,7 and 10 it is evidently visible, that the maximal volume of the chamber of type A surpasses the maximal volume of the chamber of type B which provides increase of yield of the machine or specific capacity, depending on a concrete working process. After setting macro parameters e, a, b and interposition of centers Pk and Qk the volume of chambers is singularly defined as a function of rotation angle of the rotors and does not depend on redistribution of values of radiuses pi , P2 , qi , q2 . It means that when macro parameters are set, thermodynamics, technical and volume characteristics of the machine become full invariants relative to the task of its macro parameters. Fig.11 , a-d. Rotors of disk version, as an illustration of use in the rotary machine more than one pair of gear rims. The rotors (7 and 8) contain two pairs of gear rims. The rotor (7) mounted on the shaft (11 ), contains an inner gear rim (3) of internal pair and outer rim (6) of external pair of gear rims, mounted on the hub plate (9). The rotor (8) mounted on the shaft (12), contains combined by the non-working surfaces an outer rim (4) of internal pair of gear rims and inner rim (5) of external pair of gear rims, mounted on the hub plate (10). The gear rims (4 and 5) can be executed as one whole. The rotors (7 and 8) are mounted on shafts (11 and 12) with eccentricity e. Characteristic length a can differ for different pairs of gear rims. Two pairs of gear rims on rotors of disk version can, for example, be used both as the twostage compressor, and as the turbocompressor engine. In case of the twostage compressor external pair of gear rims (5 and 6) is used as the first stage of the compressor, while an internal pair of gear rims (3 and 4) - as the second stage of the compressor. In case of the turbocompressor engine internal pair of gear rims (3 and 4) is used as compressor, and outer pair of gear rims (5 and 6) is used as turbine - expander. Fig. 12-13. An example of use of the invention in the machine used as the engine of external combustion, working on the extended indicator diagram, or as the single step compressor with an effect of a multistage compressor. Fig.12 schematically illustrates machine containing a case (13) in which the outer rotor (15) with coaxial gear rim (17) is mounted. Profile of a contact surface of gear rim (17) consists from n identical parts described on fig. 2,5,8. Inside a rotor (15), with eccentricity e the inner rotor (14) with coaxial gear rim (16) is mounted. Profile of a contact surface of gear rim (16) consists of n identical parts described on fig. 2,5,8. The rotors are designed and mounted one relative the other according to fig.3,4,6,7,9,10. The rotors are mounted with a possibility of synchronized rotation in one direction with identical speed. At rotation of rotors the contact surfaces of gear rims interacting among themselves, in such a way that the operating space within a pair of interacting gear rims is split in the area of interaction of gear rims into closed chambers of variable volume of two types - type A and type B. Area of operating space inside a pair of gear rims, in which the operating surfaces of rims do not interact, is a chamber of variable volume of the third type C. In a process of mutual displacement of the patches of interacting surfaces of gear rims, chambers type A and type B change in opposite way and stop their existence with the termination of interaction of the patches of interacting surfaces of gear rims. The opposite change of volume of chambers type A and type B means, that at the moment of a beginning of interaction of patches, of interacting surfaces of gear rims, closing chambers, one of chambers, for example, type A, has it's possible maximal volume, and the chamber, type B, has it's possible minimal volume. During rotation of gear rims occurs displacement of lines of interaction of their working surfaces and, as result, redistribution of volumes between chambers A, B and C. Thus is volume of the chamber type A, formed with initial maximal volume, continuously decreases to the minimal volume at which chamber disappears, while volume of the chamber type B, formed with initial minimal volume is continuously increases up to the maximal volume at which occurs its opening and merging with chamber C. As simultaneously there is an interaction of several pairs of teeth of gear rims, several processes are simultaneously carried out that are distinguished only by phases. Chamber C is simply connected region of space and working medium can freely flow into any part of this region. Particular feature of claimed pair of gear rims is the opportunity of the task of a required ratio between the maximal volumes of chambers of type A and of type B, in the process of designing the rotary machine. In the case of the machine there are four channels (18,19,20,21), connecting chambers of the machine by means of designated connecting devices, marked by the same numbers (18,19,20,21 ), with entrance and exit feeds and/or by devices with the possibility of capping unused channels. The connecting device (18) connects through the channel (18) external feeds with region of chamber C, in which there is a creation of chambers type B in their greatest volume. The connecting device (19) connects through the channel (19) external feeds with region of chamber C, in which there is an opening of chambers type A in their greatest volume, and their merging with chamber C. The connecting device (20) connects through the channel (20) external feeds to chambers of type B. The connecting device (21) connects through the channel (21 ) external feeds to chambers of type A. For the machine to function as the external combustion engine, the channel (20) through the connecting device (20) is connected with an input device, and the channel (21 ) through the connecting device (21) is connected with the output device of the combustion chamber (22), containing also a channel for fuel injection (23). Design of the combustion chamber (22), the communications of channels (18,19,20,21) with chambers of variable volume and with interchamber space are carried out by various known ways and thereof are marked schematically. Through the channel (18) takes place the purge by fresh air of the chamber type B at the phase of its formation (at this phase its volume is maximal). The purge by fresh air of chambers type B stops after their formation. At the further rotation of rotors of the machine, after achieving a certain degree of compression, compressed air from chambers type B through channel (20) is fed into the combustion chamber (22), where it is mixed with injected through the channel (23) fuel and where combustion accurse. The turned out working medium through the channel (21 ) is fed into chambers type A at the initial phases of their expansion. At the certain phase of expansion of chambers type A, the feed of a working medium into them stops, and the further expansion occurs only at the expense of internal energy of a working medium. After achievement by chambers type A of maximal volume, they are disconnected, merging with the chamber C, then the exhausted working medium through channel (19) is directed to an exit feed. As volume of chambers type A is grater than volume of chambers type B, the extraction of energy of a working medium in the considered scheme on value ΔPxΔV (ΔV - difference of volumes of chambers type A and B, ΔP - average pressure on phases of expansion in oversize volume of chambers type A) is grater, than in known machines with equal volumes of compression and expansion. The machine can function as the multistage compressor. For this purpose channels (18) and (19) capped, the channel (21 ) is switched by means of a connecting device (21 ) with an input feed, and the channel (20) is switched by means of the connecting device (20) with a output feed. The effect of a multistage compression is possible because through the channel (21) occurs sucking in of gas into chambers type A, after which break the gas gets into chamber C, carrying out a role of a receiver. From the chamber C gas through chambers type B, formed by closing of partial volume of the chamber C, is displaced through the channel (20) into an output feed. Since volume of chambers type A is grater than volume of chambers type B, therefor the volume of gas entering into chamber C through chamber type A is grater than the volume of gas exiting through chambers type B. It results in increase up to an equilibrium condition of pressure in the chamber C, that is chamber C acts as a preliminary stage of compressor.

Claims: CLAIMS: 1. Pair of interacting gear rims of the rotary machine including no less than one said pair of gear rims interacting with each other with creation of variable volume chambers, eccentrically located one inside the other with eccentricity e equal to the difference of the interacting surface radiuses; profile of contact surface of inner and outer gear rim has an axis of symmetry, bounded by conjugated arcs, and consisting of n>2 identical parts, conjugated among themselves; said identical part of the said inner gear rim is bounded by the arc of radius p- j , conjugated at its ends with the concentric arcs of radius q^ and of radius a+p- j , where a = p- j + q- j , said arc of radius q^ conjugated at the other end with the arc of radius b+q- j , where b >0, which is conjugated at the other end with the said arc of radius a+p- j of adjacent identical part, which completes the said gear rim profile; said identical part of the said outer gear rim is bounded by the arc of radius p 2 = p- j + e, conjugated at its ends with the concentric arcs of radius q 2 =a - p 2 and of radius a + p 2 , said arc of radius q 2 conjugated at the other end with the arc of radius b+q 2 , which is conjugated at the other end with the said arc of radius a +p 2 of adjacent identical part, which completes the said gear rim profile.

Inventors: TARAN DAVID, TARAN, DAVID
Applicants: TARAN DAVID, TARAN, DAVID
Application year: 2000
Main classification: F01C1
IPC codes: F01C1