KR20010097111A - Apparatus for utilization of vain in fluid compression and power transformation - Google Patents

Abstract

The present invention includes a rotor and a vane that rotates eccentrically in a plurality of cylinder chambers, each cylinder chamber is divided into two spaces, so that the compression or expansion of the fluid in the space in each cylinder chamber to achieve the efficiency of power conversion The present invention provides a fluid compression and power conversion apparatus using vanes with high vibration and low noise. In accordance with the present invention, the fuel mixture air is sucked in an intake chamber, which is one of two spaces formed by the rotation of the rotor. In another compression space, the compression chamber for compressing the fuel mixture air; A rotary valve unit which generates a high pressure fluid and discharges it in a timely manner by receiving the fuel mixed air compressed by the fluid compression unit in a timely manner and spreading combustion; A high pressure fluid discharged from the rotary valve part to rotate the rotor in one direction by pressurizing the rear surface of the vane in one space and to discharge residual fluid from the other space; It is composed of a timing control unit which is interlocked with the rotor shaft of the fluid power exchange unit and adjusts the operation timing between the stroke of the fluid compression unit, the rotary valve unit, and the power switching unit. The fuel efficiency is ideally high because the combustion speed is reduced and the rotation speed is easy and the combustion efficiency is high due to the high compression efficiency and power conversion efficiency.

Description

Apparatus for utilization of vain in fluid compression and power transformation}

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a power conversion device. In particular, a rotor is rotated by a pressure at which a high pressure fluid expands in a hermetically sealed space formed by a rotor and a vane rotating in a cylinder. The present invention relates to a fluid compression and power conversion apparatus using vanes having high efficiency of power conversion and low vibration and noise generation.

Hereinafter, the prior art in the field to which the present invention belongs will be described.

First, Fig. 1 is a cross sectional view of a cylinder chamber in a conventional compressor.

Currently, power conversion devices used in automobiles and ships include internal combustion engines such as reciprocating piston engines and rotary engines. In general, the internal combustion engine is a reciprocating motion of the piston or a rotational motion of the rotor by the expansion pressure of the high-pressure gas generated during the combustion of the fuel, the configuration and operation is as known to those skilled in the art.

In the reciprocating piston engine, the ignition timing of the igniter is adjusted according to the rotational speed of the crankshaft to prevent incomplete combustion, thereby sufficiently securing the time necessary for fuel diffusion. That is, when the crankshaft rotates at high speed due to the engine operating at high speed, the starting point of the combustion stroke is faster than at low speed rotation.

Therefore, the reciprocating piston type engine has a short compression stroke at high speed, and does not sufficiently compress the fuel mixture air, and the combustion stroke starts before the piston reaches the top dead center, so the expansion pressure of the high pressure gas generated by the combustion of the fuel is increased. The efficiency of power conversion is lowered by acting in a direction that impedes the arrival of the top dead center.

As described above, the reciprocating piston type engine clearly distinguishes phases between strokes in one cycle at low rotational speeds, but in high speed rotations, there is a problem in that a reduction in electric shock or efficiency occurs due to overlapping phases between strokes.

In the case of the rotary engine, there is no valve opening and closing operation, so it has low noise. However, the time allotted to each stroke is changed according to the rotational speed of the rotor. There was a drawback to not being able to allocate the minimum amount of time.

Therefore, when the rotary engine rotates at a high speed, the time allotted to the combustion diffusion time is short and incomplete combustion occurs. This incomplete combustion causes a decrease in output, increased fuel consumption and worsening air pollution.

Meanwhile, the fluid compression compressor includes a plurality of vanes that rotate together with the eccentric rotor, and the vanes are pushed toward the inner circumferential surface of the cylinder chamber by the rotational force of the rotor and the restoring force of the spring to maintain the airtight between the cylinder chamber and the vanes.

However, when the vane is pushed in the direction of the inner circumferential surface of the cylinder by the spring restoring force and the rotational force of the rotor, the contact between the vane and the cylinder chamber is not airtight. Therefore, the prior art complements the above airtightness by using a plurality of vanes.

That is, in the case of the cylinder chamber provided in the conventional compressor as shown in Fig. 1, the fluid suction section 6A, the fluid compression section 6B, the fluid discharge section 6C and other sections. At this time, the specific portion of the fluid suction section (6A) and the fluid discharge section (6C) is provided with a hole for entering the fluid, a plurality of vane grooves at regular intervals on the circumference of the rotor (3) eccentrically rotated in the cylinder chamber ( 4A to 4R are disposed, and vanes 5A to 5R are provided for each of the vane grooves 4A to 4R.

Each vane (4A ~ 4R) is pushed in the direction of the inner circumferential surface of the cylinder from the shaft center (2) of the rotor (3) by the restoring force of the spring holding the elastic force and the action force due to the rotational angular velocity caused during high-speed rotation, It maintains the tightness required for suction and compression.

However, in the case of compressing the fluid in the cylinder chamber, the intake and discharge of the fluid should be performed in all the sections of the fluid intake section 6A and in the entire section of the fluid discharge section 6C. do. Therefore, when the rotor rotates, the fluid is sucked in the fluid suction section 6A and then compressed in the fluid compression section 6B. Generally, the vane is compressed into the compression section until the relative position of the vanes reaches from 5H to 5K. From 5L, it is used as the fluid discharge section (6C).

Therefore, the compression of the fluid in the cylinder chamber is performed only in the fluid compression section 6B, and the phase angle at which the fluid is actually compressed in one rotation period of the rotor is less than 90 degrees. There is a limitation that cannot be applied. In addition, in some cases, when the fluid compression section 6B is extended to '5L' or '5M' in order to improve the compression efficiency, the fluid discharge section 6C is narrowed, so that the absolute pressure required for discharging the compressed fluid at high speed rotation is obtained. There is a problem such as not being able to secure enough time.

In the conventional compressor, since the absolute length of the vanes 5A to 5R is considerably smaller than the radius of the rotor 3, the space occupied by the rotor 3 in the cylinder chamber has a lot of compression capacity per unit volume of the cylinder chamber. There was also.

Since the compressor using a plurality of vanes according to the prior art has low compression capacity and compression efficiency per unit volume in the cylinder chamber during one rotation period of the rotor, the vane and rotor structure rotating in the cylinder chamber cannot be applied to the internal combustion engine. I could not.

Accordingly, the present invention is to overcome the problems of the conventional power conversion device as described above, each cylinder chamber by two vanes rotating around the shaft center of the rotor and the eccentric rotation in the plurality of cylinder chamber, respectively two spaces When the fluid is compressed in one cylinder chamber, the high pressure fluid generated by burning the fluid in a specific space is expanded in the cylinder of the other side, so that the power converted to rotation of the rotor is outputted. The present invention provides a fluid compression and power conversion device using vanes having high efficiency and low vibration and noise generation.

In order to achieve the above object, the fluid compression and power conversion apparatus using the vane according to the present invention, in the intake chamber, which is one of two spaces formed by the rotation of the rotor, sucks the fuel mixture air and the other one space A compression chamber for compressing fuel mixed air in the compression chamber; A rotary valve unit which generates a high pressure fluid and discharges it in a timely manner by receiving the fuel mixed air compressed by the fluid compression unit in a timely manner and spreading combustion; A high pressure fluid discharged from the rotary valve part to rotate the rotor in one direction by pressurizing the rear surface of the vane in one space and to discharge residual fluid from the other space; It is characterized in that the technical configuration consists of a timing control unit which is interlocked with the rotor shaft of the fluid power exchange unit to adjust the operation timing between the stroke of the fluid compression unit, the rotary valve unit and the fluid power exchange unit.

1 is a cross-sectional view of a cylinder chamber in a conventional compressor,

2 is a front view of a fluid compression and power conversion apparatus using a vane according to an embodiment of the present invention,

3 is a longitudinal sectional view taken along the axis of the fluid compression section and the rotary valve section;

Fig. 4A is a longitudinal sectional view perpendicular to the rotor shaft and is an exemplary view at the time of compression stroke,

Figure 4b is an illustration of the combustion stroke in Figure 4a,

4C is an exemplary view at the time of the exchange administration in FIG. 4A,

5a is a left side view of the apparatus according to FIG.

5b is a right side view of the apparatus according to FIG.

6 is a detailed view of the fluid compression unit in FIG. 4A;

Figure 7a is a detailed view of the vanes separated from the rotor,

7B is a detailed view of the seal provided in the rotor.

Explanation of symbols on the main parts of the drawings

10 engine body 10A cooling fluid part 11 intake port

12 exhaust port 15 oil pan 16 cooler full

17: distributor 20: fluid compression portion 21, 41: rotor

22, 42: rotor shaft 23, 43: vane 23C: vanes spring

24, 44: Seal 24A: Breakaway prevention groove 25, 45: Cylinder seal

25A: Intake chamber 25B: Compression chamber 30: Rotary valve part

31A: combustion chamber inlet 31B: combustion chamber exhaust 32: rotary valve shaft

33: igniter 34A: intake gas flue 34B: high pressure gas flue

35 combustion chamber 40 fluid power exchange 45A exhaust chamber

45B: power exchange chamber 51, 52: gear 53: cam

54 valve lever part 54A valve lever roller 54B valve lever spring

Hereinafter, the configuration and operation of the present invention will be described in detail based on the embodiments illustrated in the accompanying drawings.

First, Figure 2 is a front view of a fluid compression and power switching apparatus using a vane according to an embodiment of the present invention, Figure 3 is a longitudinal cross-sectional view cut along the axis of the fluid compression unit and the rotary valve, Figure 4a is a rotor shaft Fig. 4B and Fig. 4C are each an example of a combustion stroke and an exchange stroke in Fig. 4A, respectively, and Figs. 5A and 5B are left side and right side views, respectively. 6 is a detailed view of the fluid compression section in FIG. 4A, FIG. 7A is a detail view of the vanes separated from the rotor, and FIG. 7B is a detail view of the seal provided in the rotor.

As shown in each of the drawings, a suitable embodiment of the present invention, in the intake chamber (25A) of one of the two spaces formed by the rotation of the rotor 21 intake the fuel mixture air and the other one space In the compression chamber (25B) and the fluid compression unit 20 for compressing the fuel mixture air; A rotary valve unit 30 generating high pressure fluid by timely receiving the fuel mixed air compressed by the fluid compression unit 20 and expanding the combustion; The high pressure fluid discharged from the rotary valve part 30 presses the rear surface of the vane 43 in one space, thereby rotating the rotor 41 in one direction and discharging the remaining fluid in the other space. Wow; A timing control unit interlocked with the rotor shaft 42 of the fluid power exchange unit 40 to adjust the operation timing of the stroke between the fluid compression unit 20, the rotary valve unit 30, and the fluid power exchange unit 40; 51 to 54B).

The fluid compression unit 20 includes a cylinder chamber 25 divided into an intake chamber 25A and a compression chamber 25B according to the position of the vane; A rotor 21 which rotates along an axis eccentric from the center of the cylinder so that one of the outer circumferential surfaces contacts the inner circumferential surface of the cylinder, and has a seal 24 to maintain the airtightness of the contact surface; The vane 22 is interlocked with the rotor 21 and rotates on the shaft center of the rotor 21, and the vanes 22 divide the cylinder chamber into two spaces by maintaining the tip of both blades and the airtightness of the cylinder.

The rotary valve unit 30 rotates one shaft 32 so that the fuel mixed air compressed by the fluid compression unit 20 flows into the combustion chamber 35 in a timely manner, and generates the high pressure generated in the combustion chamber 35. Rotary valves 31A to 31B for allowing fluid to be discharged into the fluid power exchange unit 40 in a timely manner; It is composed of a combustion chamber 35 to generate a high-pressure fluid by combustion diffusion of the fuel mixture air introduced by the operation of the rotary valves 31A to 31B using the igniter 33.

In addition, the timing controllers 51 to 54B may include a plurality of running surfaces having different radii in order to convert the rotational movement of the rotor shaft 22 of the fluid compression unit 20 into the linear movement of the valve lever 54. A cam 53 having 53A to 53C); The valve lever part 54 rotates one axis by the valve lever roller 54A which travels the running surface of the cam 53, and opens and closes the said rotation valve 31A-31B in a timely manner.

The operation of the device configured as described above is as follows.

Appearance of the apparatus according to the present invention is the same as the general appearance of the engine, as shown in Figure 2 the engine body 10 forms the overall appearance of the engine, which can prevent the temperature rise of the engine by the heat of combustion of the fuel The cooling fluid part 10A is provided.

In addition, the intake port 11, which is a year for introducing fuel mixed with air into the fluid compression unit 20 at a ratio suitable for combustion in the vaporizer, and an exhaust port for discharging residual fluid after heat exchange is performed in the fluid power exchange unit 40. (12), a cooler flier (16) interlocked with the rotor shaft (42) of the fluid power exchange unit (40) to start the engine cooling fan, a distributor (17) for controlling the ignition time of the igniter, and the engine To supply lubricant to the rotor shaft 42 of the fluid power exchange unit 40, the rotor shaft 22 of the fluid compression unit 20, and each frictional part in the engine, which outputs the power converted by the controller to an external device. The fan 15 and the like correspond to the functional parts remarkable in the appearance of the engine.

In addition, the fluid compression unit 20 includes a cylinder chamber 25 having two holes respectively connected to the intake port 11 and the intake gas flue 34A at a predetermined portion, and is larger than the inner peripheral surface diameter of the cylinder chamber 25. The rotor 21 having a small diameter can be eccentrically rotated while contacting the inner circumferential surface of the cylinder chamber 25. At this time, the outer circumferential surface of the rotor 21 is provided with a plurality of seals 24 arranged at appropriate intervals to keep the contact surface with the cylinder inner circumferential surface airtight, the plurality of seals 24 as shown in Figure 7b The upper and lower release preventing grooves 24A are provided to prevent the separation from the rotor 21 during the high speed rotation.

Further, the vanes 23 which are disposed radially in the eccentric rotor 21 and rotate have a structure in which the tip ends of the two blades facing each other are in airtight contact with the inner circumferential surface of the cylinder. That is, as shown in FIG. 7A, the vanes 23 are provided with vanes springs 23C between the two blades so as to variably change the length between the tips of the two blades when the rotor 21 rotates. At this time, since the vanes spring 23C retains the elastic force, when one vane of the vane is pushed in the axial direction of the rotor in the cylinder chamber, the vane spring is pushed toward the inner circumferential surface of the cylinder.

The operation of vanes is such that the vane is in close contact with the inner circumferential surface of the cylinder by the rotational speed of the rotor in the conventional compressor, etc., the angular velocity acting on each vane during low speed rotation is not large enough that the air tightness between the vane and the inner circumferential surface of the cylinder chamber is not sufficient It is different from what was done.

In addition, the above operation acts on both vanes of the vanes 23 at all positions in the cylinder chamber 25, so that even if the rotation angle and the rotational speed are variable, the airtightness is not severely changed, so the design and control of the device are easy. Can be done.

In this way, the outer circumferential surface of the rotor 21, the inner circumferential surface of the cylinder and the vane 23 can form a hermetically sealed space to hold a gaseous or liquid fluid, and the fluid compression portion 20 with respect to the formed closed space. ), The space including intake gas flue 34A is referred to as compression chamber 25B, and the space constantly open to intake port 11 for intake of fuel is referred to as intake chamber 25A. At this time, the intake chamber 25A and the compression chamber 25B are mutually switched in the cylinder chamber 25 by the rotation of the rotor 21 and the vane 23, and the compression chamber is twice in one rotation of the rotor 21. 25B is formed.

The fluid power exchange section 40 is the same as the configuration of the fluid compression section 20 described above, and there is a difference in its operation. That is, the fluid compression unit 20 sucks and compresses the low pressure fluid by using power, and the fluid power exchange unit 40 rotates the rotor shaft 42 by the expansion pressure of the high pressure fluid and the low pressure residual fluid. To discharge. In this case, the spaces formed in the cylinder chamber 25 of the fluid power exchange unit 20 corresponding to the intake chamber 25A and the compression chamber 25B of the fluid compression unit 20 are respectively an exhaust chamber 45A and a power exchange chamber. This is referred to as 45B.

Subsequently, the rotary valve unit 30 will be described. The rotary valve unit 30 is roughly divided into a combustion chamber 35 and two rotary valves 31A to 31B. Each rotary valve 31A to 31B has one state open only to the fluid compression unit 20, one state open only to the fluid power exchange unit 40, and the fluid compression unit 20 and the fluid power exchange unit 40. The three states, such as one state that is not open to any of the), are switched between cycles of each cycle. The state switching of the rotary valve unit 30 is performed by the timing controllers 51 to 54B, and the operation of the rotary valve unit 30 is controlled by the rotation of the cam 53 according to the stroke.

At this time, the two rotary valves 31A to 31B rotate one shaft 32 and have a phase difference of 180 degrees with each other to alternately perform a stroke. That is, since two stroke cycles must be performed while the rotor shafts 22 and 42 of the fluid compression unit 20 or the fluid power exchange unit 40 rotate one time, two rotary valves 31A to 31B are provided. And cross-operation. To this end, the rotary valve shaft 32 has three operating states by the cams 53 on the rotor shaft 22 of the fluid compression section 20, respectively, and the cams having the three-phase running surfaces 53A to 53C. The reference numeral 53 is interlocked by the rotor shaft 42 and the gears 51 and 52 of the fluid power exchange part 40 to open and close the rotary valves 31A to 31B.

Next, the one-stroke cycle performed by the compression / combustion / exchange operation will be described.

First, in the compression stroke, the valve lever roller 54A travels the compression running surface 53A of the cam 53 and rotates the rotary valve shaft 32, thereby conducting the intake gas flue 34A and the combustion chamber intake port 31A. The fluid in the compression chamber 25B is introduced into the combustion chamber 35. As the rotor 21 of the fluid compression unit 20 continues to rotate, the fluid introduced into the combustion chamber 35 is compressed.

When the fluid in the combustion chamber 35 is compressed by the compression stroke so as to be suitable for combustion of fuel, the combustion stroke is started. In the combustion stroke, the valve lever roller 54A deviates from the compression running surface 53A of the cam 53 and travels the combustion running surface 53B, whereby fluid exchange is performed through the combustion chamber suction mechanism 31A and the combustion chamber exhaust mechanism 31B. Will be prevented. Subsequently, the fuel held in the closed combustion chamber 35 is combusted using the igniter 33 at an appropriate timing, thereby generating a high pressure gas.

At this time, the ignition time of the igniter 33 is adjusted, so as to ensure the optimum time required for the fuel diffusion of the fuel in accordance with the rotational speed of the rotor. For example, the low speed rotation may be ignited in the second half of the combustion stroke, and the high speed rotation may be controlled to ignite in the first half of the combustion stroke.

When the high pressure fluid diffuses into the combustion chamber 35 by the combustion stroke, the exchange stroke starts. In the replacement stroke, the valve lever roller 54A travels through the exchange running surface 53C of the cam 53 and rotates the rotary valve shaft 32 so that the combustion chamber exhaust mechanism 31B and the high pressure gas flue 34B are connected to each other. The fluid is introduced into the power exchange chamber 45A of the fluid power exchange unit 40. The high pressure fluid introduced into the fluid power exchange section 40 is applied to the rotor shaft 42 by applying pressure in the direction of the exhaust chamber 45A to the vane 43 due to the pressure difference between the power exchange chamber 45B and the exhaust chamber 45A. ) Is rotated in one direction.

When the high pressure fluid in the fluid power exchange unit 40 generates the proper power in the exchange stroke, the valve lever roller 54A leaves the exchange running surface 53C of the cam 53 to release the valve lever spring 64B. By returning to the compression running surface 63B with the elastic force of 1, the one stroke period is completed and a new compression stroke is started.

At this time, the one-stroke cycle described above is centered on one rotary valve 31A to 31B, and the apparatus according to the present invention includes two rotary valves 31A to 31B having a phase difference of 180 degrees and operating coaxially. While one rotary valve 31 performs an exchange stroke, the other rotary valves 31A to 31B perform a compression / combustion stroke. That is, the two rotary valves 31A to 31B alternately perform stroke cycles so that the compression / combustion / exchange stroke is performed twice in one rotation of the rotor shafts 22 and 42.

As such, the device compresses air mixed with fuel by using a rotor and vanes that are eccentrically rotated in a cylinder chamber, and timely burns the compressed air in a rotary valve unit to generate a high-pressure fluid and enter the fluid power exchange unit. In this case, the rotor shaft is rotated by the expansion pressure of the high-pressure fluid in the power exchange chamber of the fluid power exchange unit to output power.

One embodiment of the fluid compression and power conversion apparatus using the vane according to the present invention described above does not limit the technical idea of the present invention. That is, the technical idea of the present invention can constitute various embodiments through appropriate modifications and changes as well as the above-exemplified embodiments.

As described above, the fluid compression and power switching device using the vane according to the present invention, because the vanes and the rotor rotates continuously in one direction to switch the power, the structure is simpler than the conventional reciprocating piston or rotary power converter It is possible to miniaturize and improve the durability, and to reduce the noise and vibration during operation.

And in the conventional compressor, the airtightness of the compression chamber is lowered at low speed rotation, the device according to the present invention is compressed even at low speed rotation because the vane tip of the vane is in airtight contact with the inner peripheral surface of the cylinder chamber by the elastic force of the vane spring. Maintaining high airtightness in the seal has the effect of enabling highly efficient compression.

In addition, since the igniter can be operated at any time when the combustion stroke is performed, the compression stroke and the combustion stroke do not overlap even at high rotation speeds, so that sufficient time necessary for fuel diffusion is ensured, thereby enabling complete combustion of the fuel and thus fuel efficiency. And the efficiency of power conversion is improved and there is an effect that can reduce the air pollution by the exhaust gas.

Claims (6)

A fluid compression unit for sucking fuel mixed air in the intake chamber 25A, which is one of two spaces formed by the rotation of the rotor 21, and compressing the fuel mixed air in the compression chamber 25B, which is another space ( 20); A rotary valve unit 30 generating high pressure fluid by timely receiving the fuel mixed air compressed by the fluid compression unit 20 and expanding the combustion; The high pressure fluid discharged from the rotary valve part 30 presses the rear surface of the vane 43 in one space, thereby rotating the rotor 41 in one direction and discharging the remaining fluid in the other space. Wow; A timing control unit interlocked with the rotor shaft 42 of the fluid power exchange unit 40 to adjust the operation timing of the stroke between the fluid compression unit 20, the rotary valve unit 30, and the fluid power exchange unit 40; 51 to 54B) fluid compression and power switching device using a vane, characterized in that consisting of. According to claim 1, The fluid compression unit 20 and the fluid power exchange unit 40, A cylinder chamber 25 having flue for the flow of the fluid at a predetermined position; A rotor 21 which eccentrically rotates from the shaft center of the cylinder chamber 25 so that one of the outer circumferential surfaces contacts the inner circumferential surface of the cylinder chamber 25, and maintains the airtightness of the contact surface; It is interlocked with the rotor 21 and rotates about the axis of the rotor 21, the fluid tip and the power using the vane, characterized in that the front end of the blade is composed of vanes 22 to maintain the inner circumferential surface of the cylinder and airtight Switching device. According to claim 1, The rotary valve unit 30, Rotating one shaft 32 allows the fuel mixture air compressed in the fluid compression unit 20 to flow into the combustion chamber 35 in a timely manner, and the high pressure fluid generated in the combustion chamber 35 is fluid fluid power exchange unit ( 40 a plurality of rotary valves 31A to 31B to discharge in a timely manner; Fluid using a vane, characterized in that composed of a combustion chamber 35 to generate a high-pressure fluid by burning the fuel mixture air introduced by the operation of the plurality of rotary valves (31A ~ 31B) using the igniter 33 Compression and Power Conversion. The method of claim 1, wherein the timing control unit (51 to 54B), Cam 53 having a plurality of running surfaces (53A ~ 53C) of different radius in order to convert the garden motion on the rotor shaft 22 of the fluid compression section 20 to the linear motion of the valve lever portion 54 and; And a valve lever part 54 which rotates one shaft by a valve lever roller 54A traveling on the running surface of the cam 53 to open and close the rotary valves 31A to 31B in a timely manner. Fluid compression and power switching device using vanes. The method of claim 2, wherein the vanes 23, A plurality of wings disposed to face each other in a straight line on the axis of the rotor; And a vane spring (23C) for connecting the plurality of blades in a state in which elastic force is retained so that the tip of each blade is hermetically contacted with the inner circumferential surface of the cylinder chamber. The method of claim 2, wherein the rotor 21, A seal 24 which contacts the inner circumferential surface of the cylinder chamber 25 at a specific position and maintains airtightness; And a separation preventing groove (24A) which prevents the sealing (24) from being separated from the rotor (21) during the rotation of the rotor (21).