KR200343568Y1 - Trocoid gear pump - Google Patents

Abstract

The present invention relates to a trocoid gear pump. It includes a drive gear in which a plurality of trocoid gear teeth are formed on the outer circumferential surface; A first driven gear that accommodates the drive gear in an eccentric state therein and has a plurality of trocoid gear teeth formed on its inner and outer circumferential surfaces; A second driven gear that accommodates the first driven gear therein and having a plurality of trocoid gears formed on an inner circumferential surface thereof; A casing for hermetically receiving the drive gear and the first and second driven gears; A first suction port provided at a portion where the gear of the drive gear and the inner gear of the first driven gear are separated when the drive shaft rotates; A second suction port provided at a portion where the outer gear teeth of the first driven gear and the inner gear teeth of the second driven gear are separated; A first discharge port provided at a portion where the gear of the drive gear and the inner gear of the first driven gear are narrowed when the drive shaft rotates; And a second discharge port positioned at a portion where the outer gear of the first driven gear and the inner gear of the second driven gear are narrowed.

Trochoid gear pump of the present invention made as described above, by installing another driven gear between the drive gear and the driven gear constituting the trocoid gear pump is capable of two-stage compression of the working fluid can send the working fluid at high pressure Of course, the suction amount and discharge amount of the working fluid can be increased to provide a high speed and high pressure pumping performance.

Description

Trocoid gear pump

The present invention relates to a trocoid gear pump.

A trocoid gear pump is a pump employing a gear having a trocoid tooth. Usually, the conventional trocoid gear pump has an inner drive gear having a trocoid tooth formed on its outer circumferential surface, and accommodates the drive gear in an eccentric position with respect to its center of rotation. And an outer driven gear having a trocoid tooth engaged with the teeth of the drive gear, and a casing for hermetically housing the drive gear and the driven gear.

The trocoid gear pump configured as described above has a basic mechanism of changing the volume of the driving gear and the driven gear engaged therebetween and thereby sucking and compressing and discharging the fluid. It has been used as a fluid pump for decades because its structure is relatively simple and can be miniaturized.

However, since the trocoid gear pump uses only two gears, the compression ratio was limited. That is, even if the rotational torque of the drive gear is increased as much as possible, the working fluid is discharged every time the drive gear rotates one by one, so the pressure of the working fluid discharged is no longer high. Therefore, it is limited to use in the place where high head is required, and the discharge speed is also limited, which does not provide the performance of high speed pumping.

The present invention was created to solve the above problems, and by installing another driven gear between the drive gear and the driven gear forming the trocoid gear pump, two-stage compression of the working fluid is possible, and the working fluid can be sent out at high pressure. Of course, the purpose of the present invention is to provide a trocoid gear pump that provides a high speed and high pressure pumping performance by increasing the suction amount and discharge amount of the working fluid.

1 is a view schematically illustrating a configuration of a trocoid gear pump according to an embodiment of the present invention.

2 is a side view of the trocoid gear pump shown in FIG.

3A and 3B are diagrams for explaining two modes of operation of the trocoid gear pump according to an embodiment of the present invention.

4A, 4B, and 4C are diagrams showing a mechanism of operation of the gear pump in the operation mode shown in FIG. 3A.

5A to 5F show the mechanism of the operation of the gear pump in the operation mode shown in FIG. 3B.

<Explanation of symbols for the main parts of the drawings>

11: Casing 13: Trocoid Gear Assembly

14: drive shaft 15: drive gear

17: 1st driven gear 19: 2nd driven gear

21: 1st suction port 23: 2nd suction port

25: 1st discharge port 27: 2nd discharge port

29: connection pipe 31: suction pipe

33: delivery pipe

In order to achieve the above object, the present invention, a drive shaft for axial rotation by receiving an external power; A drive gear having the drive shaft fixed through the rotation center and having a plurality of trocoid gears formed on an outer circumferential surface thereof; The drive gear is accommodated in an eccentric state therein and is driven when the drive gear rotates. The inner circumferential surface of the drive gear meshes with the drive gear and is pushed by the trocoid gear of the drive gear when the drive gear rotates, and receives a plurality of rotation torques. A first driven gear having a trocoid gear tooth formed therein, the number of which is one more than that of the drive gear and the same number of trocoid gear teeth as the inner circumferential surface formed on the outer circumferential surface thereof; The first driven gear is accommodated in an eccentric state therein and driven when the first driven gear rotates. The inner circumferential surface of the first driven gear is pushed by a trocoid gear formed on the outer circumferential surface of the first driven gear to receive rotational torque. A second driven gear having a plurality of trocoid gear teeth, the number of which is one more than that of the first driven gear; A casing which sealably houses the drive gear and the first and second driven gears, and rotatably supports the drive shaft; It is formed on the side of the drive shaft of the casing and connects the inside and the outside of the casing, and when the drive shaft is driven to introduce the external working fluid into the casing and to discharge the working fluid introduced into the casing outside the casing, A first suction port provided at a portion where the gear of the drive gear and the inner gear of the first driven gear are separated when the drive shaft rotates; A second suction port provided at a portion where the outer gear teeth of the first driven gear and the inner gear teeth of the second driven gear are separated; A first discharge port provided at a portion where the gear of the drive gear and the inner gear of the first driven gear become narrow when the drive shaft rotates; And a second discharge port positioned at a portion where the outer gear of the first driven gear and the inner gear of the second driven gear are narrowed. In addition, the working fluid discharged from the first discharge port is The first discharge port and the second suction port are connected by a connecting pipe so as to flow to the second suction port and to be second compressed between the drive gear and the first driven gear. Hereinafter, one embodiment according to the present invention will be described. Detailed description will be made with reference to the accompanying drawings. FIG. 1 is a view schematically illustrating a configuration of a trocoid gear pump according to an embodiment of the present invention. Referring to the drawings, according to the present embodiment The trocoid gear pump includes a trocoid gear assembly 13 configured to be in a state where three trocoid gears are engaged with each other, and the gear assembly 13 is hermetically housed therein. It is configured to include a casing (11). The casing 11 takes the form of a cylinder having a predetermined diameter. The trocoid gear assembly 13 includes a drive gear 15 and an agent for receiving the drive gear 15 at an eccentric position therein. And a second driven gear 19 for receiving the first driven gear 17 and the first driven gear 17 at an eccentric position therein. The drive gear 15 is a drive shaft to be described later. Supported by the casing (11) through the (14) to rotate. In addition, the second driven gear 19 is rotatably provided with its outer circumferential surface on the inner circumferential surface of the casing 11. In particular, the first driven gear 17 is located in the space between the drive gear 15 and the second driven gear 19. The first driven gear 17 is in line contact with the drive gear 15 and the second driven gear 19 is outside the line. The gears 15, 17 and 19 extend by the same length in the longitudinal direction of the drive shaft 14 and have a constant cross-sectional shape. In addition, as in the conventional two-wheeled trocoid gear pump, both ends of the gear (15, 17, 19) is packed with respect to the inner wall surface of the casing 11, so that the drive gear 15 and the first driven gear ( The space formed by 17) and the inner wall of the casing 11 is sealed to the outside. Similarly, the space formed by the inner wall of the first driven gear 17, the second driven gear 19, and the casing 11 is also sealed to the outside. The drive shaft 14 is formed on the rotational central axis of the drive gear 15. Is fixed. After the drive shaft 14 completely passes through the drive gear 15, both ends thereof protrude and extend out of the casing (11 in FIG. 2) as shown in FIG. 2. The drive shaft 14 is driven. It penetrates the central axis of rotation of the gear 15 but is not in contact with or connected to the first driven gear 17 or the second driven gear 19. This configuration is the same as the two-wheeled trocoid gear pump which has been used for several decades, and the present invention differs in that another homogeneous gear is used between the drive gear and the driven gear which constitute the trocoid gear pump. The drive shaft 14 is axially rotated in the direction of arrow a by receiving power from an external power source to axially rotate the drive gear 15. That is, as the driving shaft 14 is forcedly rotated in the direction of the arrow a, the first driven gear 17 is pushed to follow and the second driven gear 19 is driven by the first driven gear 17 to follow. The internal space between the drive gear 15 and the first driven gear 17 at the portion where the suction port 21 is located becomes wider, and also the internal space between the first driven gear 17 and the second driven gear 19. The wider the pressure, the lower the pressure, and the external working fluid is sucked in. As the drive shaft 14 continues to rotate, the space between the drive gear 15 and the first driven gear 17 becomes wider, and then the second discharge port. It gets narrower as it approaches (27). At the same time, the space between the first driven gear 17 and the second driven gear 19 also becomes wider and then narrows closer to the first discharge port 25. When the inner space is narrowed, the pressure of the inner working fluid rises, so that the working fluid is discharged through the first and second discharge ports 25 and 27. The narrowed inner space starts to widen again as it moves toward the first and second suction ports 21 and 23. Thus, the space between the gears 15, 17, and 19 is continuously widened and narrowed. The center of rotation of the first driven gear 17 is eccentric with respect to the center of rotation of the second driven gear 19, and the center of rotation of the drive gear 15 with respect to the center of rotation of the first driven gear 17. Of course, the axis is eccentric. This operating mechanism itself is also the same as the conventional two-wheeled trocoid gear pump. In addition, since both ends of the drive shaft 14 pass through the casing 11 and are supported by the casing, the center of rotation of the drive gear 15 is always maintained. It is kept constant. On the outer circumferential surface of the drive gear 15, a known trocoid tooth is formed. In the present embodiment, six gears are formed. The first driven gear 17 takes the form of a hollow cylinder, and a trocoid gear is formed on the inner and outer circumferential surfaces of the first driven gear 17. The gear teeth formed on the inner circumferential surface of N) are meshed with the gear teeth formed on the drive gear 15, and the number thereof is seven more than one. The drive gear 15 and the first driven gear 17 have the same engagement structure and operation mechanism as the known trocoid gears. Gears formed on the outer circumferential surface of the first driven gear 17 are formed on the inner circumferential surface thereof. The gear corresponds to this. The gear teeth formed on the outer circumferential surface of the first driven gear 17 have the same number as the gear teeth formed on the inner circumferential surface. In addition, the gear formed on the outer circumferential surface of the first driven gear 17 is also a conventional trocoid gear. Of course, the second driven gear 19 has the outer circumferential surface relative to the casing and the gear on the inner circumferential surface thereof. Is a gear element formed. The second driven gear 19 also follows the axial rotation of the drive gear 15 and rotates in the same direction as the drive gear together with the first driven gear 17. The inner peripheral surface of the second driven gear 19 Gear teeth corresponding to gear teeth of the first driven gear 17 are formed. The gear teeth formed on the second driven gear 19 are also conventional trocoid gear teeth, and the number of gears of the first driven gear 17 is one more than that. The first and second suction ports 21 and 23 are provided at one side of the drive shaft 14 and the first and second discharge ports 25 and 27 are formed at the other side thereof. The first and second suction ports 21 and 23 are connection paths connecting the inside and the outside of the casing 11 to guide the external working fluid into the casing 11, and the first and second discharge ports 25 and 27 are A passage for discharging the working fluid compressed in the casing 11 to the outside of the casing 11. The first and second suction ports 21 and 23 are driving gears 15 when the shaft of the driving shaft 14 rotates. And the position between the first driven gear 17 and the second driven gear 19 start to open with respect to each other and the internal pressure is lowered. Therefore, when the shaft of the drive shaft 14 rotates, the working fluid flows between the drive gear 15 and the first driven gear 17 through the second suction port 23 and through the first suction port 21. It may flow between the first driven gear 17 and the second driven gear 19. The first and second discharge ports 25 and 27 may include a drive gear 15 and a first driven gear 17, respectively. The second driven gears 19 are located at a portion where the internal pressure starts to narrow with each other. Therefore, as the drive shaft 14 continues to rotate, the working fluid between the drive gear 15 and the first driven gear 17 is discharged through the second discharge port 27, and the first driven gear 17 and the first driven gear 17 are discharged. The working fluid between the two driven gears 19 is discharged through the first discharge port 25. The positions of the inlet port and the discharge port vary depending on the shape and size of each gear. It is a side view of the trocoid gear pump shown in FIG. 1. Referring to the figure, the drive shaft 14 penetrates the center part of the casing 11, and protrudes from both surfaces of the casing 11. As shown in FIG. Since the drive shaft 14 extends outside the casing 11, the drive shaft can be easily connected to a drive source such as a motor, an engine, or the like. 21 and 23 and the first and second discharge ports 25 and 27 are located. Separate suction pipes 31 and 33 of FIG. 3 may be connected to the suction ports 21 and 23 and the discharge ports 25 and 27. FIGS. 3A and 3B illustrate a trocoid gear pump according to an embodiment of the present invention. The first operating mechanism is to draw the working fluid into two suction ports at the same time and to discharge them simultaneously to the two discharge ports. The second operating mechanism is to operate The fluid is first sucked into one of the first suction ports and then discharged to the first discharge port. The working fluid discharged to the first discharge port is guided and supplied to the second suction port to be compressed again in the casing and then to the second discharge port. 3A shows the first operating mechanism described above. Referring to the drawing, a working fluid is injected into the first and second suction ports 21 and 23 in an arrow p direction,It can be seen that after being compressed around the inside of the yings 11 and discharged through the first and second suction ports 21 and 23 through the first and second discharge ports 25 and 27 in the arrow q direction. Is a suction pipe and connects the first and second suction ports 21 and 23 to the outside. Reference numeral 33 denotes a delivery pipe. The discharge pipe 33 is a passage for supplying the working fluid discharged through the discharge ports 25 and 27 to the required place. FIG. 3B is a view showing the second operating mechanism described above. As shown, the first discharge The port 25 and the second suction port 23 are connected to each other through a connecting pipe 29. Therefore, the working fluid supplied into the casing 11 through the first suction port 21 along the arrow p direction is first compressed in the casing 11 and then in the arrow q direction through the first discharge port 25. It is discharged and flows along the connecting pipe 29 and flows into the second suction port 23. The working fluid supplied to the second suction port 23 is secondly compressed in the casing 11 and then discharged to the outside through the second discharge port 27. FIGS. 4A, 4B, and 4C are shown in FIG. 3A. In order to explain the operation of the gear pump in one operation mode, it is shown in sequence. Referring to FIG. 4A, as the drive shaft 14 rotates, the gear assembly 13 rotates as a whole, during which the first and second suctions are performed. It can be seen that the gap between the drive gear 15 and the first driven gear 17 and the first driven gear 17 and the second driven gear 19 in the portion where the ports 21 and 23 are located. In this way, as the gears are separated from each other, the pressure decreases, and an external working fluid flows into the casing 11 through the first and second suction ports 21 and 23. In this state, the drive shaft 14 continues. When rotated, the working fluid moves in a state of being trapped between the gears 15, 17, and 19 as shown in FIG. 4B, and gradually approaches the first and second discharge ports 25 and 27. As described above, the gear 15 When the working fluid, which has been moved in a confined space between the points 17 and 19, finally reaches the first and second discharge ports 25 and 27 as shown in FIG. 4C, the working fluid is discharged simultaneously through both discharge ports. The mechanism itself, in which the sucked working fluid is confined between the gears 15, 17 and 19, moves to the discharge port side in accordance with the rotation of the gear, is the same as the working fluid moving mechanism in the known trocoid gear pump. This mechanism is also known through Starrotor's homepage at http://www.starrotor.com. As described above, the working fluid moves in a state of being trapped between the gears 15, 17 and 19. It is a matter of course that no flow path is provided between the suction ports 21 and 23 and the first and second discharge ports 25 and 27. Figs. 5A to 5F show gear pumps in the operation mode shown in Fig. 3B. As shown in FIG. 5A, when the driving shaft 14 is rotated, the working fluid that has been waited outside is introduced into the casing 11 through the first suction port 21. Move. The working fluid sucked into the casing 11 through the first suction port 21 is trapped between the first driven gear 17 and the second driven gear 19 toward the first discharge port 25. (See FIGS. 4b and 4c). As described above with reference to FIG. 4, the working fluid moves in a confined space between the first driven gear 17 and the second driven gear 19. FIG. same. That is, the working fluid is moved by rotation of the gear in a state of being trapped between the first and second driven gears 17 and 19, and not through any flow passage. The working fluid exits the casing 11 through the first discharge port 25 and is moved to the second suction port 23 through the connection pipe (29 of FIG. 3B). The working fluid moved to the second suction port 23 is sucked between the drive gear 15 and the first driven gear 17 as shown in FIG. 5D and thereafter, by the continuous rotation of the drive gear 15. The compressed working fluid between the drive gear 15 and the first driven gear 17 in the state shown in FIG. 5E is finally moved to the second discharge port 27 to the outside. The working fluid sucked into the space between the drive gear 15 and the first driven gear 17 is locked in the closed space between the drive gear 15 and the first driven gear 17 to prevent rotation of the gear. To go by. The principle of the fluid movement is the same as the known trocoid gear pump. As described above, the trocoid gear pump according to the present embodiment has various characteristics such that the compression of the working fluid can be achieved in two stages or the discharge speed can be quickly realized. It can be applied to the field and can be first applied to a compressor (compressor-expander), two-stage compressor, volumetric gas turbine, automobile engine, fluid pump, etc. The present invention has been described in detail through specific embodiments. The present invention is not limited to the above embodiments, and various modifications may be made by those skilled in the art within the scope of the technical idea of the present invention.

Trochoid gear pump of the present invention made as described above, by installing another driven gear between the drive gear and the driven gear constituting the trocoid gear pump is capable of two-stage compression of the working fluid can send the working fluid at high pressure Of course, the suction amount and discharge amount of the working fluid can be increased to provide a high speed and high pressure pumping performance.

Claims (2)

A drive shaft for rotating shafts by receiving external power; A drive gear having the drive shaft fixed through the rotation center and having a plurality of trocoid gears formed on an outer circumferential surface thereof; The drive gear is accommodated in an eccentric state therein and is driven when the drive gear rotates. The inner circumferential surface of the drive gear meshes with the drive gear and is pushed by the trocoid gear of the drive gear when the drive gear rotates, and receives a plurality of rotation torques. A first driven gear having a trocoid gear tooth formed therein, the number of which is one more than that of the drive gear and the same number of trocoid gear teeth as the inner circumferential surface formed on the outer circumferential surface thereof; The first driven gear is accommodated in an eccentric state therein and driven when the first driven gear rotates. The inner circumferential surface of the first driven gear is pushed by a trocoid gear formed on the outer circumferential surface of the first driven gear to receive rotational torque. A second driven gear having a plurality of trocoid gear teeth, the number of which is one more than that of the first driven gear; A casing for hermetically receiving the drive gear and the first and second driven gears and rotatably supporting the drive shaft; It is formed on the side of the drive shaft of the casing to connect the inside and the outside of the casing, and when driving the drive shaft to introduce the external working fluid into the casing and to discharge the working fluid introduced into the casing outside the casing, A first suction port provided at a portion where the gear of the drive gear and the inner gear of the first driven gear are separated when the drive shaft rotates; A second suction port provided at a portion where the outer gear teeth of the first driven gear and the inner gear teeth of the second driven gear are separated; A first discharge port provided at a portion where the gear of the drive gear and the inner gear of the first driven gear are narrowed when the drive shaft rotates; And a second discharge port located at a portion where the outer gear of the first driven gear and the inner gear of the second driven gear are narrowed. The method of claim 1, The first discharge port and the second suction port are connected by a connecting pipe such that the working fluid discharged from the first discharge port flows to the second suction port and is secondly compressed between the drive gear and the first driven gear. Gear pump.