WO1998053210A1

WO1998053210A1 - Eccentric sliding vane equilibrium rotor device and its applications

Info

Publication number: WO1998053210A1
Application number: PCT/CN1998/000078
Authority: WO
Inventors: Junyan Song
Original assignee: Junyan Song
Priority date: 1997-05-23
Filing date: 1998-05-25
Publication date: 1998-11-26
Also published as: EP1016785A4; CN1074816C; AU7519198A; EP1016785A1; CN1255186A

Abstract

This invention relates to an eccentric equilibrium rotor device applicable for fluid positive-displacement devices such as compressors, pumps, blowers or motors, having two integrally crossed and equally weighted sliding vanes fixed in the cross-shaped sliding path in the body of the hollow rotor and perpendicular to each other. At the centers of the two slides there are projecting studs provided with coupling rings by which balancing between the inertial force of the motion of the slides is obtained. This invention also relates to a rotary engine using many kinds of fuel, which is constituted by a compressor in coaxial tandem with a gas motor. Both of the said compressor and the gas motor have an eccentric equilibrium rotor with a single sliding vane, and a combustion chamber is provided therebetween and communicates with them.

Description

Sliding vane eccentric balance rotor device and its application

Technical field

The present invention relates to a sliding vane type eccentric balanced rotor device, and particularly to a sliding vane type eccentric balanced rotor device of a fluid variable capacity compressor, a pump, a fan and a motor, and an application thereof.

Background technique

In the prior art, sliding vane type eccentric rotors for pumps, compressors, pneumatic and hydraulic motors mostly use separate sliding vanes. When the rotor rotates, the centrifugal force acts on the top of the sliding vanes to move against the cylinder wall, causing great friction. Force, the sliding blade is easy to wear, increasing power consumption and shortening the life of the machine. Slip-blade eccentric rotor-type machines have long attracted the attention of the engineering community and produced many different improvements. In some aviation low-pressure oil pumps, integral penetrating vanes are used. The inner wall of the cylinder is formed by joining several segments of arcs. The stress of the vanes is better than that of non-integral vanes; US patent US, A, 4929159, 4958995 are also trying to balance the centrifugal force when the sliding blades are rotating. Its structure is complicated and it is difficult to solve the dynamic pressure of the sliding blades on the slide. The sliding blade eccentric rotor machinery is mainly used in small and medium-sized refrigerators; There have been no reports of successful sliding vane fans and heat engines.

Reciprocating piston machinery started from the bellows used in ancient Chinese metallurgy industry, and has continued to develop in the manufacture of steam engines and internal combustion engines. However, due to the limitations of its own structure, the thermal efficiency of steam engines is less than 22%, and the thermal efficiency of gasoline engines is about 26% to 40%. , The thermal efficiency of diesel engines is about 30% to 46%, and it is very difficult to further improve the thermal efficiency and specific power. In order to improve the traditional heat engine, people have explored a variety of rotary piston engines, the most famous of which is a Wankel-type rotor engine using a spinner linear cylinder. From the 1960s to the early 1970s, the aircraft was mass-produced and used in the automobile industry. However, under the dual blows of the worldwide oil crisis in the 1970s and the strengthening of environmental protection laws by governments of various countries, it gradually withdrew from the market. Very few manufacturers continued to use sports cars. The military mobile power supply and special vehicles and ships continued to develop and produce a small number of products. On the other hand, although low-power gas turbines have high specific power, good balance, and low mechanical friction power consumption, the torque and power output characteristics of the required power and speed range of the car are poor, and the high-speed range requires the matching of a new transmission Device, As a result, it is expensive, so it is difficult to become a general-purpose engine.

Summary of the Invention

One of the objectives of the present invention is to design a sliding vane eccentric balance rotor (ESVER-Eccentric Sliding Vane Equilibrium Rotor) device, which can make the inertial force between the sliding vane and the sliding vane or between the sliding vane and the balancing member Balance each other to reduce or eliminate the dynamic pressure of the top of the sliding plate on the cylinder wall and the sliding plate on the slideway, reduce frictional power consumption, and improve the sealing environment.

The second purpose of the present invention is to apply the ESVER device to an existing sliding vane refrigerator, improve its main performance indicators, and enable it to compete with other fluid variable capacity refrigerators and obtain advantages; and develop fans that use ESVER. Products and other cold products, expanding the application range of sliding blade machines,

The third purpose of the present invention is to use the ESVER device to develop energy-saving multi-fuel engines. The engine should have the combined advantages of traditional fluid-varying machines and traditional impeller machines. Compression ratio, expansion ratio, and speed, torque, and power output characteristics suitable for automobiles. It also has the characteristics of impeller machinery to separate the compression process and expansion process of the working medium, a relatively independent combustion chamber, high specific power, and balance. The thermal efficiency should be higher than the current traditional heat engines. It should be a high-performance engine with low exhaust pollution.

The ESVER device is implemented like this:

A sliding vane type eccentric balanced rotor device includes a rotor body eccentrically installed in a cylinder body, and the eccentricity is a radial slideway uniformly distributed on the rotor body, which is characterized in that: the rotor body has a hollow portion, and the rotor body has a hollow portion. The radial slideway is provided with at least a pair of equal-weight components that move perpendicular to each other, at least one of which is a whole through the slide; passes through the center of mass of the equal-weight component and is parallel to the axis of the rotor body, and has a center on the equal-weight component Short axis or shaft hole, which are connected by a movement restraint; the inertial force of the movement of the equal weight components is balanced with each other by the movement restraint.

The ESVER device of the present invention can also be implemented by the following measures:

The center's short axis or shaft hole of the equal weight component is connected by a rigid, elastic or flexible motion restraint. The movement restraining member is a coupling collar, and the coupling collar is sleeved outside a pair of central short axes of the equal weight component, and the optimal axial distance between the two central short axes is e. The motion restraining member is a connecting rod with two-way protruding short parallel shafts. The two protruding short shafts are located on both sides of the connecting rod body, and the optimal axial distance is e. One of the said equal weight parts is a whole penetrating slide, and the other is a part that plays a balancing role. To form a single sliding vane type eccentric balanced rotor device. The equal weight components are all penetrating through the sliding plate, and can form a double sliding plate, a four sliding plate, a six sliding plate, or a multi-sliding eccentric balance rotor device. The integral penetrating slide is composed of a slide frame and a slide seal or a sealing component; the slide frame includes two slide bodies, a connecting beam between the two slide bodies, and a short protruding center at the center of the connecting beam. Shaft or shaft hole; the sliding vane frame can be a single part, or an integral component processed by multiple parts through appropriate processes. The sliding vane eccentric balanced rotor device has at least one sliding vane frame; the sliding vane seal or seal assembly includes elasticity. The components and connectors include a T-shaped seal on the top of the sliding blade, a wear-resistant reed seal, and a self-expanding sealing sleeve and a self-expanding quasi-surface contact sealing sleeve that seal the entire sliding body. The rotor body may have a half hollow portion or a single hollow portion or a plurality of hollow portions. The sliding vane type eccentric balanced rotor device is used in various compressors, pumps, fans, and motors. An energy-saving multi-fuel rotor engine uses a sliding vane eccentric balanced rotor compressor and a sliding vane eccentric balanced rotor gas motor to be coaxially connected in series, and communicates with a combustion chamber.

Overview of the drawings

FIG. 1 is a first embodiment; a schematic view of a double sliding blade ESVER compressor, a vacuum pump, or an air motor;

FIG. 2 is a comparison diagram of the pressure distribution of the sliding plate on the cylinder wall in the prior art and the ESVER device; FIG.

Figure 4 is a schematic diagram of a sliding plate in an ESVER machine;

Figure 5 is a schematic diagram of seven ESVER slides and sealing schemes;

Figure 6 is a layout diagram of a typical ESVER hollow rotor body and sliding blades;

Fig. 7 is a second embodiment; a schematic diagram of a double-slide ESVER fan and a large air motor; Fig. 8 is a third embodiment; a schematic diagram of a double-slide ESVER liquid pump and a hydraulic motor; Fig. 9 is a fourth embodiment; Picture of ESVER scheme;

Fig. 10 is a fifth embodiment; a schematic view of a single-slide ESVER gas motor or compressor; Fig. 11 is a sixth embodiment; a double-slide ESVER perspective view of a constraining member is a connecting rod; Fig. 12 is a seventh embodiment; Expansion ESVER steam motor schematic diagram;

FIG. 13 is an eighth embodiment; a schematic diagram of an ESVER energy-saving multi-fuel rotor engine; FIG. 14 is a working principle diagram of the ESVER engine. Best Mode of the Invention

FIG. 1 is a first preferred embodiment of the present invention; a double-slide ESVER compressor, a vacuum pump, or an air motor. In FIG. 1, there are a pair of equal-weight slides which are penetrated and arranged vertically in the rotor body slideway. The slide S1 is in the vertical position and the slide S2 is in the horizontal position. The rotor body is a two-piece assembly with a cavity in the middle. S1 is like a vertically symmetrical I-shaped, the upper and lower parts are sliding body, the narrow middle part is the connecting beam, on both sides of the middle of the connecting beam, parallel to the axis of the rotor body And along the central axis of the sliding plate, there are central short axes al 'and al "each protruding outward; the sliding plate S2 (S2' and S2") resembles two narrow I-shapes (only seen in Figure 1-A To the cross section of the connecting beam), the width of the sliding body and the connecting beam are only half that of the vertical sliding plate, and the sum of the weights of the two horizontal sliding plates is equal to the vertical sliding plate. The two horizontal sliding plates are put together and the middle part is formed A rectangular hole parallel to the axis of the rotor body and along the central axis of the sliding plate, each has a central short axis a2 'and a2 "protruding inward. Since the sliding blades SI and S2 are center-symmetrical parts with uniform mass distribution, their centers of mass must be at the intersections of their respective central axes and the central cross section of the cylinder block. The central cross section of the cylinder block is also the plane of motion of the centroid of the sliding sheet. The diameter of the central short axis of the sliding plate is i, and R1 and R2 are two coupling collars, which are respectively set on the outer sides of the two pairs of central short axes, and the inner diameters thereof are Z) = e + i /, — general ί <¾, so that The maximum axial distance between the two center short axes is e.

The above-mentioned rotor equipped with the sliding blade and the coupling collar is eccentrically installed in an approximately isosinusoidal cylinder body, and the eccentricity is ^ A seal arc is processed at the tangent of the rotor and the cylinder body; The sealing sheet groove is filled with a graphite or Teflon sealing sheet F which can slide freely in the radial direction. The entire rotor is supported by front and rear cylinder heads and bearings and can be flexibly rotated. When the external torque drives the rotor to rotate clockwise at an angular velocity ω, the right air inlet draws air, and after the gas is compressed in the variable volume chamber, it is output from the left air outlet. As the rotor rotates, the vane is essentially making planetary movements: that is, the mass center of the vane revolves around the central axis (virtual axis) of the coupling ring at an angular velocity of 0) _g , and at the same time, the vane revolves around its central short axis to The angular velocity ω rotates, and the revolution has a relationship with the rotation angular velocity o) _g = 2ω; the rotation axis of the sliding blade coincides with the central axis of the center short axis (or shaft hole) of the sliding blade, and the sliding blade (or balance piece) and the coupling shaft The rings together form the planetary rotating mass system with the central axis of the coupling ring as the revolution axis. The inertial forces of this group of heavy sliding blades will be balanced by the coupling ring. The top of the sliding plate is against the cylinder wall and the sliding plate is generally against the slideway. No more dynamic pressure. The force condition of the sliding blade is improved, and the friction power consumption is reduced. Low, while also obtaining a better sealed environment. When the suction port is connected to a fixed container, the machine is a vacuum pump. When a gas with a certain pressure is input from the outside into the cylinder (left side air intake, right side exhaust) to drive the rotor to rotate, and the shaft outputs power, the machine is pneumatic motor.

Figure 2 shows the comparison of the pressure distribution of the sliding plate on the cylinder wall in the prior art and the ESVER device: The traditional separate sliding plate has dynamic pressure on the entire cylinder wall (Figure 2-A), and the traditional penetrating sliding plate is under the cylinder body. The half part has dynamic pressure (Figure 2-B). When the sliding plate in the ESVER device is not equipped with a sealing plate, the top of the sliding plate rarely contacts the cylinder wall, and the cylinder wall will not be subject to dynamic pressure (Figure 2-C).

Figure 3. The plane isosceles curve and its characteristics. The four end points of a pair of sliding blades in the above rotor create the basic contour line of a ESVER mechanical cylinder in a planetary rotation. A spinning wheel line. Figure 3-A shows a plane isosine curve of λ = = 4; Figure 3-B shows a family of plane isosine curves when λ changes from 2 to 8.

The equation of the Cartesian coordinates of the isosceles curve is:

χ = (Β-e-Sit) CosG

y = (B-e-Sin0). SitW

Its polar coordinate equation is:

p = B — e. SinO

In the above formula, and are generally constants, and 0 is an angular variable, where:

One is called the polar radius, which is equal to one-half of the horizontal chord length, and one-half of the theoretical length of the whole sliding plate. The pole diameter is IB.

e-eccentricity is the distance between the center axis of the rotor body and the center axis of the cylinder body, and it is also the optimal axial distance between the center short axes of the equal-weight components (wholes running through the sliding plate or the balance piece).

The rotation angle of a rotor body is also the rotation angle that passes through the slide as a whole.

λ—referred to as radial deviation ratio, λ = B / e

There are two important characteristics of the isochronous curve:

(1) The arbitrary chord length across the pole center is always equal to the fixed length 18. Based on this characteristic, the curve family is named as an isosine curve. This feature guarantees that the fixed-length sliding blade can freely rotate around the pole center (that is, the central axis of the rotor body) in the cylinder body with the isosceles curve as the inner wall of the main wheel. The theoretical gap can be constant equal to zero or kept at a constant minimum. (2) The locus of the midpoint P of any chord line passing through the pole center (usually also the centroid of the slider) is a circle with a diameter of g; therefore, the distance between the midpoints of any two chord lines passing through the pole center and perpendicular to each other is constant equal. This feature provides an inertial force that uses a rigid coupling ring, or other rigid, elastic, or flexible coupling to connect the central axis (rotation axis) of a group of said equal-weight components, constrain its movement, and cause it to move A balanced theoretical basis.

Figure 4. Schematic diagram of the integral penetrating slide in the ESVER machine; the integral penetrating slide in the ESVER machine is mainly composed of a slide frame and a seal. To distinguish it from other types of slides, it is a slide holder. As shown in Figure 4-A, the slider frame is I-shaped and consists of a central short axis a connected to " ¹ connected beam b" and two slider bodies v and v 'to form a whole; four pieces and two pieces can be used. A set of relative splicing is shown in Figure 4-B, which constitutes a pair of ESVER slides that are perpendicular to each other in Figure 7. Since the slide frame is subjected to alternating loads, it should be made of tough materials and processes that are resistant to fatigue. The surface of the short axis and the sliding body should be wear-resistant; the inertia distance of the sliding frame to the O-O axis and the M-N axis is zero, which will have the best mass distribution and balance effect, otherwise between each group of sliding plates The connecting piece should be installed so that it forms a seal groove on the top of the slide body as a whole, and the seal piece F made of abrasion-resistant material is installed; the seal plate groove can also be opened on the end surface of the slide body, and the installation End face seal or corner piece (various sealing schemes of Wankel rotor machine are available for reference). Wave springs can be installed in the seal groove to enhance the sealing effect of the seal at low speed.

Figure 5.Seven different ESVER slides and sealing schemes

Figure 5-A, no seal sliding blade; the sliding blade is only composed of a sliding blade holder, which can be used in liquid pump machinery; it is generally not recommended because it is prone to leakage and requires high processing accuracy.

Figure 5-B. Simple sealing strip solution. A sealing strip groove is processed on the top of the sliding body and a long sealing strip, referred to as a sealing strip, is used. The sealing strip can expand and contract in the radial direction of the sliding plate to compensate for gaps and wear. Advantages: Simple and easy to manufacture. Suitable for various compressors, pumps, fans and motors; Figure 1 uses this scheme.

Figure 5-C, T-shaped seal solution; T-slots are machined on the top of the sliding body and T-shaped seals are installed. The seals can slide in the radial direction, but the amount of wear compensation is a limited value. The curved cylinder makes the machine run in for a period of time, and the sealing gap tends to a stable value. The seal and the inner wall of the cylinder will be in a quasi-contact state, which is suitable for large size and high speed ESVER mechanical seals.

Figure 5-D, wear-resistant reed seal scheme; the composite spring is fixed on the top of the sliding body, it is best to cooperate with the approximate isosinusoidal cylinder, and the inner wall of the cylinder should be sprayed with PTFE.

Figure 5-E, F, G, and H are self-expanding seal vanes and are the recommended solutions for trial production of engines. Their common features are: The main sliding surface of the slider is composed of a separate slider cover seal. The angled part like a "jaw" has elasticity, and the outer sides of the "jaw" can be restored to a parallel state under pressure. And can be installed in the rotor body slide. Leave enough clearance between the sealing sleeve and the slide body to prevent the parts from getting stuck when they are thermally expanded. The sealing and wear compensation of the two sides of the sliding blade are guaranteed by the elasticity and self-expansion of the sliding sleeve seal. Elastic elements can be installed in the sliding vane body to increase the pressure on the top of the sliding vane sleeve facing the cylinder wall; the sliding vane sleeve can expand and contract in the radial direction, which can form a seal between the sliding vane top and the cylinder wall and compensate for wear.

Figure 5-E, simple self-expanding sealing sleeve scheme; can be used in the initial trial production to observe the sealing effect and wear. It can also be used with wedge-shaped corner piece seals to enhance the sealing of the sliding face.

Figure 5-F, column top self-expanding sealing sleeve scheme; the top corners of the seal are changed to rollers, sliding friction is changed to rolling friction, and fixed hard alloy or corundum wear parts can also be installed on the top .

Figure 5-G and H are self-expanding quasi-surface contact sealing sleeve schemes; the top of the sealing sleeve is equipped with a wear-resistant sealing pin that can rotate at a certain angle, and the line contact of the seal is converted into an approximately cylindrical contact with the cylindrical surface, or It is called quasi-surface contact seal, which is convenient for oil film lubrication, and it is helpful to reduce or avoid the formation of cylinder wall vibration. Figure 5-G shows the position where the radial axis of the sliding blade coincides with the axis of symmetry of the cylinder block, as shown in Figure 13-B. At this time, the pressure angle between the sliding blade and the cylinder wall is zero degrees; The vertical position of the cylinder axis of symmetry is shown in Figure 13-A. At this time, the pressure angle between the sliding plate and the cylinder wall reaches the maximum.

Figure 6, Typical ESVER hollow rotor body and sliding blade arrangement scheme; the sliding blades in the figure are simplified to the form of Figure 5-A, seals and coupling rings are omitted and not shown; different hollow rotor bodies and sliding blades can There are many combinations, and only the most typical examples are given here.

Figure 6-A, arrangement scheme of semi-hollow rotor body, sliding vane and coupling collar; the figure shows a semi-hollow ESVER device (referred to as abbreviation for short) consisting of a semi-hollow rotor body, two sliding vanes and a coupling collar 2S1R); SI and S2 in the figure are the same equal weight vertical slide and horizontal slide respectively. The center short axis a of the two slides is fitted with a collar R, and the inertia of the slides to the O-O axis and M-N axis is required. The moments are all zero to ensure a good balance of the entire rotor. The semi-hollow rotor body and the half shaft with cross grooves are supported by two bearings. The sliding blade and coupling ring assembly can be easily inserted into the semi-hollow from the right side. Rotor body; The structure is simple and suitable for small refrigerator products such as electricity; water tanks, air conditioners.

Figure 6-B. Two-piece spliced hollow rotor body and single-slide and double-slide ESVER device. It is the most typical ESVER device. There are various types of sliding blade and coupling arrangement schemes. 2S2R, as shown in Figure 1, Figure 7, Figure 8;-two-ring type-1S2R, as shown in Figure 10, Figure 13.

Figure 6-C, Four-slide type ESVER device; there are two types of sliders in the figure, two of each type, two pairs of top and bottom, the four sliders are evenly distributed in the rotor body, the difference is 45 degrees, that is, the composition A four-piece two-ring ESVER device, referred to as 4S2R, was required; the inertia moments of the sliding plate to the O-O axis and the M-N axis were all zero to ensure a good balance of the entire rotor. The four-chip machine also has four-chip three-ring type-4S3R as shown in Figure 9, and four-chip four-ring type-4S4R and other solutions.

Figure 6-D. Six-piece three-ring ESVER device. Separate the split slides on the two sides of the four-piece three-ring rotor of Figure 9 separately, extend the slide body to the same width as the rotor body, and place six pieces. The slides are evenly distributed, and each of them is at an angle of 30 degrees, forming a six-piece three-ring type ESVER device as shown in Figure 6-D. Regarding the ESVER device, the following points need to be explained:

(1) ESVER is a planetary rotating mass system composed of multiple parts, not a simple rigid body. It can be proved by mathematical mechanics or geometric methods that although the center of mass of the entire mass system of the eccentric rotor deviates from the axis of rotation, the center of mass is always constant during rotation. Keep relatively stationary, thus becoming an eccentrically balanced rotor.

The core of the ESVER device is: at least a pair of equal weight parts (wholes that pass through the sliding plate or the balance piece) that move perpendicular to each other are installed in the radial slides of the rotor body, which pass through the center of mass of the equal weight parts and parallel to the rotor An axis, each of the equal weight components has a rotation axis, and there is a central short axis or a shaft hole on the equal weight component along the rotation axis, which are connected by a movement restraint; as the rotor body rotates, the equal weight The components will perform self-balanced planetary motion, and their inertial forces are balanced with each other by the motion constraint.

(2) The main characteristics of the ESVER device are: the central short axis or shaft hole of the equal weight component is connected by a rigid, elastic or flexible (such as an endless chain or a steel wire rope) movement restraint, and the specific connection is The formula depends on the structure, size and working conditions of the actual machine.

(3) Coupling ring is the most simple and practical central axis movement restraint; when the central short axis diameter of the equal weight parts is equal and is the best inner diameter of the coupling ring is generally less than ¾; the inner ring of the coupling ring The surface must be abrasion-resistant, and overall requires high strength and toughness.

(4) The position of the central axis of the equal weight component can also be made into a shaft hole, and then a fixed pin is press-fitted; or a bearing is installed in the shaft hole, and the movement restraining member is a connection having a bidirectionally protruding parallel short shaft. The two short shafts of the rod are located on both sides of the connecting rod body, and the optimal shaft distance is e; the shaft diameter of the two connecting rods can be matched with the bearing and can be flexibly rotated.

(5) In ESVER machinery, it is possible to use a isosceles curve, an approximate isosceles curve or a standard cylindrical cylinder (theoretical radius of the cylinder R _Be = ^ B ^{2 +} e). Practice has proved that: ESVER operates in a circular cylinder. Flexible and stable, with good balance, tightness and processability.

(6) A pair of mutually perpendicular sliding blades, one of which can also be derivatized into a balance piece or a balance guide for pure balance, which can form a single sliding blade eccentric balance rotor device.

(7) In actual machinery, a pair of vertical sliding blades can be used to form a model that divides the cylinder into four variable-volume chambers, or two or three pairs of vertical sliding blades can be formed uniformly. Models with the cylinder divided into 8 or 12 variable-capacity chambers, as shown in Figures 6-C, D; Models larger than 12 cavities or odd-numbered sliding blade models can also be made, but the structure is too complicated and the practical value is not Big.

(8) In the future, when ESVER machinery gradually increases speed and enlarges the external dimensions, the sliding blades should be made of high-strength alloy precision casting into hollow parts (similar to the gas turbine blade process), or high-strength lightweight materials of aircraft wings, which are bonded and welded. Or riveting and other processes to make the combined slide, so that it has high fatigue strength and the smallest possible quality.

(9) ESVER is suitable for the development of various compressors, pumps, fans, pneumatic and hydraulic motors, etc., which can reduce energy consumption, reduce specific weight, and extend service life; this type of machinery has excellent rotor speedup and capacity expansion. It has a huge capacity-enhancing potential to expand the size of the body, which can increase the displacement of the sliding vane machine by a factor of ten, or even ten times, or tens of times, which will help expand the application range of the sliding vane machine.

(10) ESVER should also be applied to high-efficiency rotor steam and gas motors whose working medium is high temperature, high pressure steam or gas, which converts thermal energy into mechanical energy. Can also be used for development with high thermal efficiency Rate of many forms of engines.

FIG. 7 is a second embodiment of the present invention, a double-slide ESVER fan and a large air motor; a pair of integral through-sliders are spliced together with four identical sliders, as shown in FIG. 4 -B, with two Coupling rings are balanced with each other. Fans can be made using Figure 5-B, C, and D slides. This structure can also be used to make double-slide ESVER steam or gas motors. Only the working medium is changed to pressure steam or gas. In order to reduce the corrosion effect of high-temperature water vapor and reduce frictional power consumption, the entire cylinder block, cylinder head, rotor body, sliding Teflon should be sprayed on the film slot and sliding sleeve cover. When the gas temperature is too high, the cylinder block should be water-cooled. This structure can be used in multiple stages to manufacture high-pressure compressors, or as an intermediate test machine for multi-stage ESVER high-pressure steam motors. It can also be used independently as a drive motor for blast furnace blowers or blast furnace gas residual pressure power generation or geothermal steam power generation.

Figure 8 is a third embodiment of the present invention, a double slide ESVER liquid pump and hydraulic motor; the structure is the same as Figure 7, because the liquid is incompressible, the import and export are appropriately modified; Figure 5-A, B, C. D can be used during manufacturing Type slide. When the external power drives the rotor to rotate clockwise, the liquid is drawn in from the right port and discharged from the left port. It is a liquid pump or a fixed pump. When pressure oil is input from the right port and the rotor is driven clockwise to output power, the machine will be an oil motor. ; When the clean water in the reservoir is used to drive it to rotate, the machine will be a water motor; if multiple cylinders are connected in series to stagger the inlet and outlet, and the water pressure of the main bearing is balanced, it is possible to manufacture a water-saving ESVER 'water turbine, . When used for oil transfer pumps, in order to reduce flow pulsation, a four-chip machine solution or an accumulator can be installed in the pipeline; this solution is suitable for heavy oil pumps, gas-liquid two-phase pumps for oil and gas mixed transmission, and water and oil Two-phase pumps and other special applications. In order to reduce the corrosive effect of water and frictional power consumption, the entire cylinder block, cylinder head, rotor body, sliding slot and sliding sleeve should be sprayed with PTFE or made of anti-corrosive material.

Fig. 9 is a schematic diagram of a four-slide, three-ring type gas compressor according to the fourth embodiment; two uniformly-arranged vertical penetrating slides are installed in the rotor body, and it is required to be 45 in the figure. The mass distribution of the equal weight sliders S3 and S4 in the angular position can ensure that the center of mass is located at the intersection of its central axis and the central cross section of the cylinder block, and the inertia force of the two sliders can be balanced by the middle coupling ring R1; the slider Sl S2 and S2 are balanced with each other through coupling rings R2 and R3. The four-chip machine has multiple structural solutions. Because the cylinder is divided into eight chambers, it is beneficial to increase the compression ratio and reduce repeated compression.

FIG. 10 is a fifth embodiment of a single-slide ESVER gas motor (a compressor in reverse operation); There is only one sliding blade in the rotor, and the other sliding blade is converted into an equal-weight balanced guide post. The two top surfaces of the guide post no longer extend beyond the cylindrical surface of the rotor body, so the length of the seal line is reduced, and Have a large compression ratio or expansion ratio; when used as a compressor, a check valve is generally installed at the exhaust port, or an exhaust groove is opened on the cylindrical surface of the rotor body. When the predetermined compression ratio is reached, the The gas communicates with the exhaust port through the exhaust groove and exhausts; at other corners, the exhaust port is closed by the cylindrical surface of the rotor. When used as a gas motor, the length of the air intake groove or the corresponding angle of rotation of the cylindrical surface of the rotor body determines the expansion ratio of the gas. This solution can be made independently, but the main purpose is to serve as an intermediate test machine for ESVER engines.

FIG. 11 is a sixth embodiment; a perspective view of a double slide ESVER of a constraining member is a connecting rod, showing that the sliding parts S1, S2 have a shaft hole in the central part, and the central axis movement constraining member is a connecting rod with a bidirectionally protruding parallel short axis L, The optimal axial distance between the two short axes is equal to c. The shaft diameter of the two short axes should be able to cooperate with the central shaft hole of the two slides and be able to rotate flexibly. The inertial forces of the two slides can be balanced with each other by this link. This solution is suitable for batch products that can directly die-cast the central shaft hole of the sliding blade.

FIG. 12 is a seventh embodiment; a schematic diagram of a multi-stage expansion ESVER steam motor. The high-temperature and high-pressure steam supplied from the boiler Q first enters the first stage in the center. After expansion work, it enters the steam superheater H to warm up, and continues to expand to the end of the outer side. In the first stage, the exhausted steam and water will be recycled back to the boiler and turned into high temperature and high pressure steam for reuse. The main structural features of the machine are:

ESVER air motors are symmetrically arranged. The high-pressure stage bores are small and are located in the center. The cylinder bores at all levels extending to both sides are gradually increased. The low-pressure stage bores are the largest and located at the outermost sides. The adjacent cylinders are installed 180 degrees apart. The intake and exhaust ports are alternately and symmetrically arranged. As long as the diameter and length of the rotor are properly designed, the radial gas pressure acting on the main bearing of the rotor will be reduced or eliminated. In this model, the radial pressure of the gas on the rotor in the high-pressure stage can be well balanced. Since a better thermodynamic cycle can be selected, it can also have higher thermal efficiency at low and medium speeds. With the gradual reduction of world petroleum resources, using coal or nuclear energy as an alternative energy source to drive large ships may create conditions for the development of large multi-level ESVER steam engines. The reverse operation of this scheme can be used to make high-pressure compressors.

FIG. 13 is an eighth embodiment of the present invention; it is a schematic diagram of the development of an energy-saving multi-fuel rotor engine using an ESVER device; the foregoing ESVER structure principle and embodiment are mainly for development Show preparations for the ESVER engine. The ESVER gas compressor and the ESVER gas motor are coaxially connected in series, and a variety of engines can be formed by communicating with the combustion chamber. Figure 13 is an engine designed with a single vane ESVER device; Figure 13-A is a single vane gas The cross section of the motor, Figure 13-B is a cross section of a single vane compressor, Figure 13-C is a vertical section of the whole machine. The single vane ESVER compressor (Figure 13-C-I) has the same structure as a unit Only the cylinder and the width of the sliding blade are increased to f times (f = 1.2 ~ 2, f = 1.4 in this figure) the gas motor (Figure 13-C-II) coaxially connected in series, and the cross section of the two engine block The symmetrical central axes PQ and XY are perpendicular to each other. On the angle bisector of the two central axes and on the tangent side of the rotor body and the cylinder body, a long cylindrical combustion chamber 3 is provided parallel to the longitudinal axis of the cylinder body. An injection nozzle 2 is provided at the left end of the combustion chamber, which can inject a variety of Fuel. There are two spark plugs 1 above the combustion chamber. The volume of the combustion chamber is 8 for the compressor, and 11.2 (8 X 1.4) for the gas motor. An inlet passage 5 is provided on the lower right side of the combustion chamber to communicate with the compressor, and an outlet passage 4 is provided on the lower left side of the combustion chamber to communicate with the gas motor. An air inlet is provided on the lower right part of the compressor. On the cylindrical surface of the rotor body of the compressor, two air inlet grooves are opened in a clockwise direction from both sides of the sliding vane to extend about 75 °. An exhaust port is provided on the upper left of the gas motor; on the cylindrical surface of the rotor of the gas motor, the opening is continued from the two sides of the vane in a counterclockwise direction for about 105. Two air vents at the corners.

FIG. 14 is a schematic diagram of the working principle of the ESVER engine; (A-A) and (B-B) in the figure correspond to the cross-sectional views of A-A, B-B in FIG. 13, which respectively represent the gas motor and the gas compressor. Exaggerated combustion chambers are horizontally drawn above them. The left and right ends of the combustion chamber are connected to the compressor and the gas motor with inlet and outlet channels. The left end of the combustion chamber is painted with an injector and two spark plugs are on the top. The rotor in FIG. 14 is simplified into a rotor body with inlet and outlet slots and a single sliding blade that can move freely, and other structures are not shown. When the engine is rotated in a clockwise direction, the sliding plate and the rotor body always divide the cylinder body into 2 to 3 independent and closed variable volume chambers. The compressor will complete the suction and compression process, and the gas motor will complete the expansion work and exhaust process. The detailed working process is shown in the figure: Assume that the two sliding blades are in the horizontal position at the beginning, and the rotation angle of the sliding blades is zero degrees as shown in the figure. 14-A. When the starter motor drives the serial main shaft of the engine to rotate clockwise, the half-concave space of the upper half of the compressor vane will gradually decrease with rotation, and the gas will be compressed. When turning to an angle of about 55 ° and the gas pressure in the compression chamber is about 0.4 MPa, the air intake on the cylindrical surface of the rotor body The tank is connected to the combustion chamber intake channel as shown in Figure 14-B, and new air begins to enter the combustion chamber. At the same time, the gas in the combustion chamber that has not been discharged during the previous combustion process and has a pressure of 0.25 to 0.35 MPa is squeezed into the expansion chamber of the gas motor through the air outlet channel. The air inlet channel that communicates with the compressor and the air outlet channel that communicates with the gas motor At the same time, the opening angle is about 10 ° (this angle needs to be experimentally optimized), which is called the overlap angle of the scavenging gas of the combustion chamber. As the rotor continues to rotate, the extruded gas will freely expand and work in the chamber at the lower right of the gas motor, as shown in Figure 14-C. In this process, the outlet passage of the combustion chamber to the gas motor will be closed by the cylindrical surface of the rotor body and maintained at a rotation angle of about 75 °. At the same time, the gas in the compressor will continue to be pressed into the combustion chamber, and the sealed adiabatic compression process will be gradually completed. . When the compression ends, the original left end of the sliding blade enters the rotor seal area, and the inlet and outlet channels of the combustion chamber are closed. The fuel injection nozzle injects (the injection can be advanced, and the optimal injection advance angle needs to be determined by experiments). The spark plug ignites As shown in Figure 14-D; during the ignition and explosion combustion period, the combustion chamber heats up and rises under near-constant volume conditions. Bypassing the angle of 20 ° ~ 30 ° again, when the compressor and the gas motor's sliding blades turn to an angle of about 160 °, the air outlet groove on the cylindrical surface of the gas motor rotor body connects the combustion chamber with the expansion chamber of the gas motor as shown in Figure 14. -

E. High-pressure gas is continuously introduced into the expansion chamber of the gas motor, pushing the sliding blade through the horizontal line at an angle of 180 °, and maintaining the gas introduction connection angle of 90 ° ~ 100 ° from the beginning of the expansion. The pressure of gas expansion continuously pushes the sliding The work is performed until the next sweep of the combustion chamber, squeezing all the gas into the expansion chamber, and closing the gas outlet channel of the combustion chamber again. The gas in the expansion chamber of the gas motor continues to expand freely to perform work until the slide reaches the horizontal position again and expands. When the chamber volume reaches the maximum value, as shown in Figure 14-F, the pressure in the expansion chamber is close to atmospheric pressure, that is, the pressure potential energy of the gas has been used to the maximum. Subsequently, the sliding blade continued to rotate. When the 360 ° angle was bypassed, the expansion chamber communicated with the exhaust port, and the exhaust gas was discharged as shown in Figure 14-B. At the same time that half of the rotor volume is exhausted, the other half of the rotor volume begins the next expansion and work process.

It can be seen that, for each revolution of the machine's series spindle, the compressor will complete two suction and compression processes, the combustion chamber will complete two inflation, explosive combustion and high-pressure working gas output processes, and the gas motor will complete two expansion operations. The work and exhaust gas exhaust process; that is, each revolution of the engine's main shaft will complete two work cycles of suction, compression, combustion expansion work and exhaust exhaust gas.

The following points need further explanation:

(1) The four strokes of suction, compression, expansion, and exhaust of reciprocating engines and Wankel engines are The suction and compression of the ESVER engine are performed in the first-stage cylinder, and the expansion and exhaust are performed in the second-stage cylinder. The middle is connected by an independent combustion chamber. The two coaxially connected two The rotor has good balance and forms a "blade" with a vane whose working surface is retractable together with the vane. This structure is more similar to a gas turbine. On the other hand, in small and medium models and in the general engine speed range, its The essence of working fluid movement and thermal power conversion still belongs to fluid varactor. From the perspective of its structural layout and thermal power conversion, ESVER engines will be a new type of heat engine between traditional reciprocating machines and impeller machinery.

(2) Continuously improving the thermal efficiency of the engine is an eternal theme of heat engine development and research; the present invention sets the ratio of the maximum expansion volume of the gas motor to the maximum suction volume of the compressor to 1.2 ~ 2 (the specific value depends on the degree of intake air pressure), This is beneficial to make full use of the pressure potential energy in the gas, reduce the exhaust temperature, and improve the thermal efficiency of the whole machine. In the experimental research of the rotor engine, it was found that due to the unidirectional flow characteristics of the gas working medium and without the obstruction of the intake and exhaust valves, the exhaust temperature was higher than that of the traditional reciprocating piston engine. The exhaust gas temperature is about 900, and the heat energy taken up by the exhaust gas accounts for about 43% of the total thermal energy. Although the exhaust gas temperature of the reciprocator is slightly lower, the energy taken out by the exhaust gas is also considerable. Energy is converted into useful work. One way is to use an exhaust gas turbocharger. The present invention is to increase the expansion working volume, make full use of the pressure potential energy in the gas, allow it to fully expand, and reduce the exhaust temperature to below 500. This alone has the potential to increase thermal efficiency by more than 10%. Because there are no moving parts in the independent combustion chamber, it can have a better combustion chamber shape and area-to-volume ratio, which is convenient to use high-temperature-resistant materials, and it is convenient to spray insulation on the surface or use ceramic combustion chambers with low thermal conductivity. The frequency is four times that of a normal single-cylinder 4-stroke engine.The combustion chamber is highly utilized and the heat loss is reduced. When the same amount of fuel is injected, the combustion temperature and pressure are high, which is conducive to the full combustion of the fuel and improves the exhaust. Quality, reducing pollution; there are multiple solutions for this type of model, which can make fuller use of the thermal energy of combustion, and it is possible to further increase the thermal efficiency.

(3) ESVER engines will have excellent dynamic balance performance, low vibration, low frictional power consumption, and high mechanical efficiency. These advantages are particularly prominent at high speeds.

(4) The curvature of each point of the cylinder block in the contour line of the approximate isosine curve is small, and the angle (or pressure angle) of the normal between the seal and the contact point of the cylinder wall is small; 8 The curve has two inflection points. Relatively speaking, the cylinder of the ESVER engine is easier to manufacture and easier to seal. In the present invention, a self-expanding sealing sleeve and a quasi-surface contact self-expanding sealing sleeve are designed (Figure 5- G, H) instead of the wiper line contact seal of the Wankel machine to form a gas pressure gradient along the length of the sealing surface, it should have a good sealing effect and avoid the occurrence of chattering on the cylinder surface.

(5) Because the pressure between the pressure of the vane in the cylinder and the rotor arm is larger,

The ESVER engine will have good torque output characteristics and low specific fuel consumption at medium and low speeds.

(6) Once the development of a multi-cylinder series high-power low-medium speed ESVER spark plug ignition diesel engine can be started, the proper layout of the multi-cylinder inlet and exhaust ports should be designed so that the radial gas pressures acting on the cylindrical surface of the rotor body mutually Balance, so that the force of the rotor main bearing is at a minimum; for high-power engines, as the body line size increases, the ratio of the length of the seal line to the working volume will gradually decrease, the sealing effect is better, and it may become a diesel locomotive and a ship Engine.

(7) This machine adopts injection fuel supply system, which is not only convenient to test and use multiple fuels, but also to use computer technology to optimize the fuel injection combustion process to save fuel.

Test and Outlook

The first ESVER test compressor used steel sliding blades and double coupling collars to test run at three speeds of 825, 1460, and 2600r / min, with displacements of 2.2, 4, and 7m ³ / min respectively. During the test, ESVER turned smoothly. Flexible, the top surface of the sliding blade frame and the inner wall of the cylinder have no traces of contact friction, low potential for vibration capacity; the same

. '' The second ESVER test compressor also uses steel sliding blades; the displacement is 11.5m ³ / min at 1470r / min, and the displacement is approximately 22m ³ / min at 2920r / min. Trial production of small compressors, vacuum pumps, oil-free compressors and medium-sized compressors with a displacement of 30 m ³ / min and a pressure of 0.8 MPa, fans and oil transfer pumps with a displacement of 150-300 m ³ / min, gas-liquid two-phase pumps, etc. prototype.

Because the ESVER device is not only an eccentrically balanced rotary piston, but also has the main characteristics of a fluid variable capacity machine; it also looks like a fully balanced eccentric impeller (the blades can expand and contract), and it also has some of the main characteristics of an impeller machine, so it may be suitable for the development of similar A variety of general machinery products for the above two types of machinery. Due to its simple structure and good processability, the ESVER device will first be used in various compressors, pumps, fans and air motors (including large-scale power generation using blast furnace gas residual pressure). Gas motor) and other products, and will gradually promote and expand the scope of application. Through continuous improvement in structure, materials and manufacturing processes, its speed and external dimensions will gradually increase. ESVER will likely be used in vehicles, ships, power generation and even aircraft, etc. It is possible to form a new type of mechanical system between traditional piston machinery and traditional impeller machinery.

Claims

Rights request

1. A sliding vane type eccentric balanced rotor device, comprising a rotor body eccentrically installed in a cylinder body, the eccentricity is e, and the rotor body has a uniform radial slideway, which is characterized in that: the rotor body has a hollow portion, At least a pair of equal-weight components that move perpendicular to each other are installed in the radial slide of the rotor body, and at least one of them is integrally penetrating the sliding piece; passing through the center of mass of the equal-weight components and parallel to the axis of the rotor body, The component has a central short axis or a shaft hole, which are connected by a movement restraint; the inertial forces of the movement of the equal weight components are balanced with each other by the movement restraint.

2. The sliding vane-type eccentric balance rotor device according to claim 1, characterized in that: the central short axis or the shaft hole of the equal-weight component is connected by a rigid, elastic or flexible movement restraint.

3. The sliding vane-type eccentric balanced rotor device according to claim 1, characterized in that: the movement restraining member is a coupling collar, and the coupling collar is sleeved outside a pair of central short axes of the equal-weight components, so that The optimal axial distance between the two central short axes of the constraint is ^

4. The sliding vane-type eccentric balance rotor device according to claim 1, wherein: the movement restraining member is a link having two-way protruding parallel short axes, and two protruding short axes are located on both sides of the link body, and The best axial distance is

5. The sliding vane-type eccentric balanced rotor device according to claim 1, wherein: one of said equal-weight components is a whole penetrating sliding vane, and the other is a part that plays a balancing role, and can form a single sliding vane. Eccentric balance rotor device.

6. The sliding vane-type eccentric balanced rotor device according to claim 1, characterized in that: the equal weight components are integrally penetrating the sliding vane, and can form a double sliding vane, a four sliding vane, a six sliding vane, or a multiple sliding vane. Plate type eccentric balanced rotor device.

7. The sliding vane-type eccentric balanced rotor device according to claim 1, wherein: the integrally penetrating sliding vane is composed of a sliding vane frame and a sliding vane seal or a seal assembly; the sliding vane frame includes two sliding vanes Body, a connecting beam between two slider bodies, and a protruding short axis or shaft at the center of the connecting beam Hole; The sliding blade frame can be a single part or an integral component processed by multiple parts through appropriate processes. The sliding blade type eccentric balanced rotor device has at least one sliding blade frame; the sliding blade seal or seal assembly includes an elastic element and a connection. There are T-shaped seals on the top of the sealing slide, wear-resistant reed seals, and self-expanding sealing sleeves and self-expanding quasi-surface contact sealing sleeves that seal the entire sliding body.

8. The sliding vane type eccentric balanced rotor device according to claim 1, wherein: the rotor body may have a half hollow portion or a single hollow portion or a plurality of hollow portions.

9. The application of the sliding vane eccentric balanced rotor device according to claim 1 in various compressors, pumps, wind turbines and motors.

10. An energy-saving multi-fuel rotor engine uses a sliding vane eccentric balanced rotor compressor and a sliding vane eccentric balanced rotor gas motor connected in series coaxially, and communicates with a combustion chamber.