MXPA00010475A - Improvements relating to rotary piston machines - Google Patents

Abstract

A rotary piston machine adapts the Stirling principle and can operate as an engine or a heat pump. Two variable volume units (1, 4) have n-lobed chambers (3, 6) rotatable about a common axis at a first speed. Each chamber contains an (n+1) sided piston (2, 5), these being rotatable about a different common axis at a different second speed, and cooperating with the lobes to form expanding and reducing sub-chambers. The first to second speed ratio is (n+1):n ducts (10, 11) incorporating regenerators provide intercommunication between the chambers (3, 6) and are open and closed by the relative piston rotation to exchange fluid or vapor between units. Heating may be provided for one unit, the expansion unit (1), and cooling for the other, the compression unit (4), and the ducts can also incorporate heating and cooling means.

Description

IMPROVEMENTS RELATED TO ROTATING PADLOCK MACHINES Field of the Invention The present invention relates to rotary piston machines. This is related to an adaptation of the Stirling principle, with rotating multi-sided pistons that operate in chambers with epitrochoidal lobes, passing the operation of fluid or vapor through closed thermodynamic cyclic processes. The machine can operate as an engine or as a heat pump.

Summary of the Invention. According to the present invention, there is provided a fluid or steam rotary piston machine that includes two units of variable volume, each unit having a rotary epitrochoidal chamber with multiple lobes and a rotary piston with multiple sides therein, forming a plurality of sub-chambers through their cooperation with the periphery of the associated chamber, the number (n + 1) being greater than the number of sides of the plunger that the number (n) of epitrochoidal arcs, where the two chambers are restricted to rotate at a first common speed around a first effective common axis, while the two pistons are restricted to rotate at a second common speed about a second effective common axis, where n + 1: n is the ratio of the first to the second common speeds, where each camera has a plurality (n) of double function ports that allow the connection between the cameras through duc coughs, and where said ducts each contain a regenerator, it being possible for one unit of variable volume to perform the collection, expansion and ejection, while the other unit performs the collection, compression and ejection, as a result of the relative rotation and the positions of the port. Preferably, the cameras will be coaxial, as will the rotors. Although in theory, you can be in different axes but coupled to rotate in relation. The term "cash" is intended to cover this alternative. Heating means can be provided for the variable volume unit, which performs the expansion processes, and there could additionally be heating means between each of said regenerator and the variable volume unit, which performs the expansion processes. Cooling means may also be provided for the variable volume unit which performs the compression processes, and there may additionally be cooling means between each of said regenerator and the variable volume unit that performs the compression processes. In the preferred form n = 2, in order that there are three tilted pistons operating in double lobed chambers. The expansion unit which may, although not necessarily, be heated, will have its ports positioned in such a way that the chambers formed therein, generally increase in volume when they are not in communication with a port, and generally decrease in volume when said • cameras are in communication with a port. The other, the compression unit which can, although not necessarily, be cooled, will have its ports placed in such a way that the chambers formed therein will generally decrease in volume when it is not in communication with a port, and increase in volume generally when said cameras are in communication with a • 10 port. The processes of operation, therefore, occur in isolated chambers of the port openings, although the transfer of operation of fluid or steam occurs between a pair of cameras, each in communication with ports that open a common pipeline. In the high-grade heat transfer is carried out so that the The fluid or vapor operation flows to, from or is contained within the expansion unit while low-grade heat transfer is achieved from the operation of fluid or vapor flowing to, from or contained within the unit expansion, the machine behaves like a motor, with an output of mechanical operation. If the mechanical operation is applied to the rotating components, but the low-degree heat transfer is carried out for the region of the expansion unit while the high-grade heat transfer occurs from the region of the compression unit , the machine behaves like a heat pump or as a refrigeration machine.

Brief Description of the Figures For a better understanding of the present invention, it will be • reference below by way of example, to the accompanying drawings, in which: Figures 1, 2, 3, 4 and 5 are schematic diagrams showing the relative positions of expansion and compression units of a machine rotary piston at intervals during a rotation cycle; and Figure 6 is a diagrammatic cross-section through a preferred embodiment of the machine.

Detailed Description of the Invention. An expansion unit 1, has a rotary piston 2 contained in a chamber 3 and a compression unit 4 has a rotary piston 5 contained in a chamber 6. Each piston 2 and 5 are generally of a flat equilateral triangle, but with the sides of the triangle convex and arcuate. Each chamber 3 and 6 is also flat, surrounded by the confines of the piston faces, and is of epitrochoidal shape of two lobes. Therefore, cameras have major and minor axes that intersect at right angles at their centers. The two units 1 and 4 are rigidly linked to rotate around a common axis through their centers, in the same direction and at the same speed, the axes being larger than the cameras 3 and 6 to 90 ° one of the other. The two rotary pistons 2 and 5 are also rigidly linked to rotate about a common axis through their centers in the same direction and at the same speed, these two thirds of the rotation speed of the cameras 3 and 6. The arcuate sides 2a, 2b and 2c of the plunger 2 are positioned 180 ° from the sides of counterpart 5a, 5b and 5c of the other piston 5. Plungers 2 and 5 operate in conjunction with the profiles of the chambers 3 and 6, to form sub-chambers 3a, 3b and 3c and 6a, 6b and 6c, of variable volume and shape in operation, as will be described later. The ports 7 and 8 in the expansion unit 1, are diagonally opposite each other, are offset by 30 ° in the direction of movement (in the clockwise direction as seen in Figures 1 to 5) , of the minor axis of the chamber 3. The corresponding ports 9 and 10 are similarly positioned in the compression unit 4, but are offset 30 ° in the opposite direction from the rotation of the minor axis of the chamber 6. This positioning ensures that during operation, a port 7 or 8, open to a sub-chamber when said sub-chamber is at a maximum volume in the expansion unit 1. Similarly, a port 9 or 10 is closed to a sub-chamber when said sub-chamber is at a maximum volume in the compression unit 4. Port 7 of the expansion unit is connected by an interconnection pipe 1 1 to the port 9 diagonally opposite compression with reference to the axis of rotation of units 1 and 4, while the port of the expansion unit 8, is similarly linked through an interconnecting duct 12 to the port of the compression unit 10 These ducts each contain a regenerator (not shown). The sequence of operation is as follows: In Figure 1, the heated operation fluid or steam occupies sub-chamber 3a, which is at a minimum volume and is open, through port 8 to line 12. sub-chamber 3b is isolated and increased in volume. The sub-chamber 3c is decreased in volume, thereby ejecting the operating fluid or vapor through port 7, through the pipeline 1 1. The fluid or vapor is left, in the case of an engine, or accepted in the case of a heat pump, with the heat inside the regenerator in said duct 1 1. The cooled operation flow or steam occupies the chamber 6a which is at a maximum, isolated volume and around to begin its compression cycle. Sub-chamber 6b is in its compression cycle, is decreased in volume and isolated. The sub-chamber 6c is increased in volume and is opened through port 9 to the pipeline 1 1. Therefore it is receiving the operating fluid or vapor from the sub-chamber 3c. The port 10 is closed by the piston 5. In Figure 2, the pistons 2 and 5 have rotated 30 ° clockwise and the cameras 3 and 6 have rotated 45 °. The sub-chamber 3a is increased in volume and accepting the operating fluid or vapor, through port 8, from duct 1 1 and sub-chamber 6b, which continues to decrease in volume and now communicates with port 10. The sub-chamber 3b, continues to increase in volume, with the heated operation fluid or steam isolated therein, being expanded while the fluid or steam transfer of continuous operation from sub-chamber 3c to sub-chambers 6c through port 7, duct 1 1, and port 9. The operating fluid or steam cooled in sub-chamber 6a, remains isolated and compressed as the volume of said sub-chamber decreases. In Figure 3, the pistons have rotated through 60 ° from their initial positions and the chambers 90 °. The sub-chamber 3a continues to increase in volume, although the piston 2 closes the port 8, thus ending the entry of the operation fluid or steam, while the expansion process begins within the sub-chamber. The sub-chamber 3b has reached its maximum volume, and the operating fluid heated therein, has reached the end of its expansion process, while the sub-chamber 3c continues to decrease in volume with the exit of the fluid or steam in operation, to through port 7, duct 1 1 and port 9 to compression unit 4. Cooled operation fluid continues to be compressed in sub-chamber 6a isolated as the volume in it decreases. Sub-chamber 6b is in the minimum and open volume, through port 10, to duct 12, but the operating fluid or vapor ceases to flow due to closure of port 8. Sub-chamber 6c continues to increase in volume and accept fluid or operation steam, through port 9, coming from sub-chamber 3c. In Figure 4, pistons 2 and 5 have moved another 30 ° and the • cameras 3 and 6 other 45 °. The sub-chamber 3a is isolated and increasing in volume, with the operating fluid heated therein, continuing its expansion process. The sub-chamber 3b now communicates with the port 8 as it is discovered by the plunger 2, since the sub-chamber is decreasing in volume, the operating fluid or steam in it is pushed out in • 10 the duct 12. The sub-chamber 3c continues to decrease in volume, and the transfer of operating fluid or steam, through port 7, duct 1 1 and port 9, continues to the compression unit 4. Sub-chamber 6a it remains isolated and decreasing in volume, with the operating fluid or steam cooled in it, continuing its compression process. The sub-chamber 6b is now increasing in volume and, due to its communication with the port 10, accepts the operating fluid or vapor from the sub-chamber 3b through the duct 12. The sub-chamber 6c continues to increase in volume and continues the influx of the fluid or operation steam through the port 9 and duct 1 1 from expansion unit 1. In Figure 5, the pistons are 120 ° from their original positions and the chambers are 180 ° from theirs. The sub-chamber 3a continues to increase in volume, with the heated operating fluid isolated therein, continuing its process of expansion. The sub-chamber 3b continues to decrease in volume, with its operating fluid or vapor passing through port 8, the duct 12 and port 10 to sub-chamber 6b which is increasing in volume. Sub-chamber 3c is in a minimum and open volume • through port 7, to duct 1 1, but the plunger of compression unit 5 has port 9 closed, and the operating fluid or vapor ceases to flow. Sub-chamber 6a is still isolated and decreasing in volume, with the operating fluid cooled therein at the end of its compression process. Sub-chamber 6b, continues to accept the transfer fluid or steam transferred • 10 from expansion unit 1. The sub-chamber 6c, now isolated due to the closing of port 9, is at the maximum volume with the fluid or steam operating therein at the beginning of its compression process. The situation inside the machine is now similar to that in Figure 1, although several bodies of fluid or vapor of operation occupy different spaces for those that are in the previous diagram. The body of the operating fluid cooled in sub-chamber 6a of Figure 1 should be considered at the beginning of its compression process. As units 1 and 4 rotate through 180 ° and the rotary pistons 2 and 5 rotate through 120 °, the relative rotor rotation will be 60 ° in the opposite direction. This finds the body of the fluid in sub-chamber 6a at the end of its compression process, in a situation similar to that of the operating steam or fluid cooled in sub-chamber 6b in Figure 1. After about an additional 30 ° of relative rotor rotation (corresponding to the positions in Figure 3), sub-chamber 6a will be at the minimum volume, and the main proportion of the operating fluid or steam that was there will have to be transferred to the sub-chamber 3c through port 9, ducts 1 1 and port 7, absorbing in the case of a motor, or rejecting, in the case of a heat pump, heating during this passage through duct 1 1. At this point, where the total rotation of the relative rotor is 90 °, the plunger 2 will have passed the port 7. The expanding sub-chamber 3c, allows the expansion of the operation fluid or steam heated therein, until some 60 ° additional rotation of the relative rotor (making the total of 150 °), when the sub-chamber 3c is in the maximum volume. The additional rotation does not cover the port 8, allowing the exit of the heated operation fluid or steam through the duct 12, in which it is cooled in the case of a motor, or heated in the case of a heat pump. Subsequently, it enters sub-chamber 6c through port 10, this transfer process occurring around an additional 90 ° of relative rotor rotation, then 240 ° in total, when sub-chamber 3c will be at the minimum volume. Plunger 5 now covers port 10 and the thermodynamic cycle comprising this particular fluid or steam body is repeated.

The processes can be tabulated around 360 ° of relative rotor rotation, corresponding to 720 ° rotation of the plunger and 1080 ° rotation of the chamber, as set forth in Table 1 below.

The closed thermodynamic cycle described above occurs and repeats, with phase displacement, with four main bodies of fluid or operating steam. In Figure 1, these are located in the sub-chamber 6a at the beginning of the compression, 5 in the sub-chamber 6b towards the end of the compression, in the sub-chambers 3c and 6c and the duct 1 1 passing through regenerative transfer and in the sub-chamber 3b that goes through expansion. The residual operating fluid or vapor in sub-chamber 3a is waiting to be mixed with the main body of the operating fluid or vapor • 10 that is in sub-chamber 6b. It will be noted that the operation processes in both expansion and compression units are of equal duration, that is 60 ° of relative rotor rotation. The regenerative transfer of operating fluid or steam coming from the compression unit 4 to the expansion unit 1, it is always towards a subchamber of non-similar designation, which is from 6a to 3c, from 6b to 3a and 6c to 3b, and is of short duration, i.e. ° rotation of the relative rotor. The regeneration transfer of operating fluid or steam from the unit expansion 1 to the compression unit 4, it is always to a subchamber of similar designation, that is, from 3a to 6a, from 3b to 6b and from 3c to 6c, and is long-lasting, ie 90 ° rotation of the relative rotor. If units 1 and 4 are of equal size, which is not necessary, the geometry ensures that the latter transfer occurs under a constant totalized volume.

The regenerative transfer of any main body of operating fluid or steam is always carried out alternatively between the two pipelines 1 1 and 12. That is, the transfer • from one unit to the other through a pipeline, it is always 5 followed by the transfer of return through the other pipeline. Due to the pairs of sub-chambers during such transfers, any main body of the operating fluid or vapor will eventually be transported through each sub-chamber within the machine, allowing rapid balances to be achieved. • 10 mass and energy of the operating fluid or steam. The route followed by a main body of the operating fluid or steam can be tabulated by approximately 720 ° of relative rotor rotation, corresponding to 1440 ° of piston rotation and 2160 ° of rotation of the cover, as shown below in Table 2. The main body of the operating fluid or steam under study in said table is that which appears in sub-chamber 6a of Figure 1, at the beginning of its compression process. It can be seen that three complete thermodynamic cycles pass before it returns to said sub-chamber 6a, after passing through the other sub-cameras of the machines. A second main body of the operating fluid or vapor which appears in sub-chamber 6b in Figure 1, which undergoes its expansion process, will follow an identical route to that shown in Table 2, with a phase shift of + 360 ° relative rotor rotation of the one shown in the Table 2. A third main body of the operating fluid or vapor which appears in sub-chamber 6b in Figure 1, was at the end of its compression process, which will follow a similar route but, with the pipelines exchanged so that the expansion unit for the transfers of the compression unit are carried out through the pipeline 1 1, while the inverse transfers are made through the pipeline 12, with a phase shift of + 180 ° of relative rotor rotation of the which was shown in Table 2. The fourth main body of the operating fluid or vapor in which sub-chamber 3c and 6c appears and in pipeline 1 1 in Figure 1, which • 10 pass through regenerative transfer to the compression unit, follow an identical route to that of the third main body of fluid or steam, with a phase shift of -180 ° of relative rotor rotation from that shown in Table 2. Therefore, the machine provides a total of twelve thermodynamic cycles during the period defined by 1440 ° rotation of the piston, corresponding to 2160 ° rotation of the chamber and 720 ° rotation of the relative rotor. It should be noted that each individual thermodynamic cycle occurs during a period defined by 240 ° rotor rotation relative, this is 480 ° of rotation of the plunger and 720 ° of rotation of the chamber. Any component, either the coupled pistons 2 and 5 or the coupled units 1 and 4, is used as the motor operating output medium or the pump operating output medium, the thermodynamic cycles have a longer duration long than those that occur in conventional reciprocal heat engines and in reciprocal heat pumps. Therefore, this must occur 360 ° from the rotation of the output or input shaft. This characteristic of the rotary machine described above, • allows improved heat transfer processes, making it possible for the ideally ideal thermodynamic cycle to be achieved. In Figure 6, the two units 1 and 4 are rigidly coupled by a hollow shaft 13 in 14 and 15 in a fixed assembly 16. The plungers 2 and 5 are carried by a common axle 17 stump in 18 and 19 in assembly 16. Ports 7, 8, 9 and 10 • 10 are on the flat radial sides of the chambers 3 and 6, near their peripheries, and are open and closed through the flat faces of the pistons 2 and 5. A gear coupling 20 between the shafts 13 and 17, ensures that units 1 and 4 rotate relative to plungers 2 and 5 in the manner described. 15 Units 1 and 4 can be encapsulated or stored to distinguish regions of higher and lower temperature around them, each unit having a large surface area for efficient heat transfer. The rotation of said units promotes an almost uniform temperature distribution. In addition to maintaining a temperature differential between units 1 and 4, there may be additional heating and cooling means for ducts 1 1 and 12 provided, for example, by adapting the encapsulation or storage to store the ends of the ducts . Any means of Additional heating will be between the regenerators and the unit 1, while any additional cooling medium will be between the regenerators and the unit 4. Figure 6 shows, for simplicity, the two isolated rotating structures. To make it work there must of course be a connection to one or another or put it to work, in the case of a bomb. Axes 13 and 17 can be adapted appropriately. It will be understood that although a simple modality with three-sided pistons operating in two-lobed chambers has been described, there may be more distributions with pistons with sides n + 1 (n> 2) in lobed-n chambers connected by a corresponding number of ducts with regenerators. The relative rotation speeds of the chambers to the pistons will be n + 1: n. ro Ni O Ul n cn or cn cn TABLE 2 or '/, or 30/45 60/90 90/135 150/180 150/225 180/270 210/315 240/360 270/405 302/450 330/495 360/540 360/450 390/585 420/630 450/675 480/720 510/765 540/810 570/855 600/900 630/945 660/990 690/1035 720/1050 720/1080 750/1125 750/1170 810 / 1215 840/1260 870/1305 900/1350 930/1395 960/1440 990/1485 1020/1530 1052/1575 1030/1630 1080/1620 1110/1665 1140/1710 1170/1755 1200/1800 1230/1845 1260/1890 1290 / 1935 1370/1980 1350/2025 1380/2070 1440/2115 1440/2150 The names indicate the rotation of the plunger followed by the corresponding rotation of in degrees Comp: Regen Compression Preocess: Expan Regenerative Transfer Process: Expansion Process 3a, 3b, 3c: Identification of Expansion Number 6a, 6b, 6c: Compression Number Identification

Claims (7)

1. CLAIMS Having described the present invention, it is considered as a novelty and, therefore, the property contained in the following CLAIMS is claimed as property: 5 1 .- A rotary fluid or steam piston machine that includes two units of variable volume, having each unit a rotary multi-lobe epitrochoidal chamber and a multi-sided rotary piston therein, forming a plurality of • 10 individual sub-chambers by its operation in conjunction with the periphery of the associated chamber, the number (n + 1) of the sides of the greater piston by one than the number (n) of the epitrocoid arcs, wherein the two chambers are restricted to rotate at a common first speed about a first common axis 15 effective, while the two pistons are restricted to rotate at a second common speed around a second common axis • effective, being the ratio of the first to the second speeds com unes n + 1: n, where each camera has a plurality (n) of
2. 2. - A rotary piston machine as described in claim 1, further characterized in that heating means are provided for the variable volume unit, which performs the expansion processes.
3. 3. - A rotary piston machine as described in Claim 2, further characterized in that additional heating means are provided between each of said regenerator and the variable volume unit which performs the expansion processes.
4. 4. - A rotary piston machine as described in Claim 1, 2 or 3, further characterized in that cooling means are provided for the variable volume unit which performs the compression processes.
5. 5. - A rotary piston machine as described in claim 4, further characterized in that additional cooling means are provided between each of said regenerator and the variable volume unit which performs the compression processes.
6. 6. - A rotary piston machine as described in any of the preceding Claims, wherein n = 2.
7. 7. - A rotary piston machine substantially as described above with reference to the drawings accompanying the present invention. • •