KR101218502B1 - Oil pump - Google Patents

Abstract

PURPOSE: An oil pump is provided to uniformly deliver oil by preventing the vortex of the oil and cavitation and forming a groove in a space between an outer surface of an inner rotor and an inner surface of an outer rotor. CONSTITUTION: An oil pump(100) comprises an outer rotor, an inner rotor(140), a first oil valve chamber(114a), a second oil valve chamber(114b), and an anti-vortex groove(160). The outer rotor is rotationally installed in a body(110), and comprises a rotary chamber inside. The inner rotor is eccentrically installed to the outer rotor, and rotated by the driving shaft of an engine. A plurality of vanes(144) are radially connected to the outer surface of the inner rotor. One end of the vane is in contact with the inner surface of the outer rotor to supply oil to a supply line. The first oil valve chamber supplies the pressure of the oil to the outer rotor to change the position of the outer rotor. The second oil valve chamber supplies the pressure of the oil supplied from the first oil valve chamber to a spring support unit(122) to change the position of the outer rotor. The anti-vortex groove prevents cavitation noise caused by the vortex of the oil when the oil is supplied.

Description

Oil Pump

The present invention relates to an oil pump, and more particularly, to an oil pump that prevents the vortex and cavitation of the oil flow inside the pump during operation of the pump.

The oil pump supplies oil to each part of the engine for smooth operation of the engine.

The oil pump is configured to apply pressure to the oil using mechanical energy of a prime mover such as an electric motor, an internal combustion engine or a steam turbine, and then move it to each part of the engine.

The oil pump has gear type, vane type and piston type according to the structure. In addition, the oil pump includes a constant delivery pump in which the discharge amount of the pump is always constant according to the load change, and a variable delivery pump in which the discharge amount is changed according to the load change.

As the vane type, the variable displacement vane type oil pump whose discharge amount is changed according to the load change is elastically supporting the inner rotor which rotates according to the rotation of the main body and the drive shaft, the outer rotor and the outer rotor which are installed eccentrically with the inner rotor. Representative components include a support spring for keeping the inner rotor eccentrically positioned and a plurality of vanes rotating in contact with the inner circumferential surface of the outer rotor to feed oil to the outside.

Here, the plurality of vanes are slidably coupled radially to the outer circumferential surface of the inner rotor, so that the distance to the central axis of the inner rotor is variable during rotation of the inner rotor.

When the inner rotor rotates, the vane pressurizes the oil, and vortices of the oil are generated at both sides of the vane, and the pressurization of the oil is uneven.

Accordingly, the present invention has been invented to solve the above problems, and when the variable capacity vane type oil pump is operated, grooves are formed on the space side between the outer circumferential surface of the inner rotor and the inner circumferential surface of the outer rotor, so that the oil It is an object of the present invention to provide an oil pump for preventing the generation of vortices and the occurrence of cavitation so as to uniformly pump oil.

In order to achieve the above object, the present invention provides a suction line for sucking oil from the oil pan, and a body having a supply line for supplying the oil introduced from the suction line to each friction portion of the engine; An outer rotor rotatably installed inside the body and having a rotary chamber formed therein; It is installed so as to be eccentric with respect to the outer rotor and rotates in association with the rotation of the drive shaft of the engine, and coupled radially slidably to the outer circumferential surface so that one end rotates while contacting the inner circumferential surface of the outer rotor to feed the oil into the supply line. An inner rotor including a plurality of vanes; A support spring having one end in contact with a spring support formed on an outer surface of the outer rotor and the other end in contact with an inner surface of the rotary chamber, for supporting the outer rotor; A first oil valve chamber formed inside the body and configured to change a position of the outer rotor by applying a pressure of oil supplied from the outside to the outer rotor; A second oil valve chamber formed inside the body and configured to change a position of the outer rotor by applying a pressure of oil supplied from the first oil valve chamber to the spring support; A bypass passage for supplying oil from the first oil valve chamber to the second oil valve chamber; And it provides an oil pump comprising a vortex preventing groove formed on the inner surface of the body covering the outer rotor and the side of the inner rotor.

The vortex preventing groove may be formed in an arc shape.

The vortex preventing groove may be positioned to contact both sides of the end of the vane.

Both ends of the vortex preventing groove may be formed to be narrower than the middle portion.

According to the present invention, a groove is formed in the space side between the outer circumferential surface of the inner rotor and the inner circumferential surface of the outer rotor during operation of the variable displacement vane type oil pump to prevent the generation of oil vortex and cavitation on both sides of the vane. Pressing can be made uniform.

In addition, since the oil feeding is made uniform, the generation of noise can be reduced.

1 is a view showing the configuration of an oil pump according to a first embodiment of the present invention.
2 is a view showing the configuration of an example of the vortex preventing groove according to the first embodiment of the present invention.
3 is a sectional view taken along line AA of FIG. 1.
4 and 5 are views showing the operation of the oil pump according to the first embodiment of the present invention.
6 is a view showing the pressure state of the oil pump according to the first embodiment of the present invention and the oil pump according to the prior art according to the rotation speed of the engine. In Figure 6, line A1 represents the pressure of the oil pump according to the prior art, line A2 represents the pressure of the oil pump according to the present invention.
7 is a view showing the torque state of the oil pump according to the first embodiment of the present invention and the oil pump according to the prior art according to the rotation speed of the engine.
8 is a view showing the configuration of an oil pump according to a second embodiment of the present invention.
9 is a perspective view showing the configuration of the outer rotor used in the oil pump according to the second embodiment of the present invention.
10 is a plan view showing the configuration of an outer rotor used in the oil pump according to the second embodiment of the present invention.
11 and 12 are views showing the operation of the oil pump according to the second embodiment of the present invention.

Hereinafter, embodiments of the present invention will be described in detail with reference to the accompanying drawings.

1 is a view showing the configuration of an oil pump according to a first embodiment of the present invention.

Referring to FIG. 1, the oil pump 100 according to the first embodiment of the present invention includes a body 110, an outer rotor 120, an inner rotor 140, a support spring 130, and a first oil valve chamber ( 114a), the second oil valve chamber 114b, the bypass flow passage 127 and the vortex prevention groove 160.

Body 110 is formed with a suction line (not shown) for sucking the oil from the oil pan, and a supply line (not shown) for supplying the oil introduced from the suction line to each friction portion of the engine. A predetermined oil valve chamber 114a is formed at a predetermined position on one side of the body 110 to allow oil to flow in and out from the suction line and the supply line.

The oil introduced into the body 110 is supplied to each part of the engine through a supply line, and then bypassed to bypass the first oil valve chamber 114a, which is a space between the body 110 and the outer rotor 120. Is supplied. The pressure of the oil supplied to the first oil valve chamber 114a is applied to one side of the outer rotor 120 to be described later to change the eccentricity of the outer rotor 120 and the inner rotor 140 to be described later.

A second oil valve chamber 114b is formed at a predetermined position on one side of the body 110 in which oil flows into the first oil valve chamber 114a according to the oil pressure in the first oil valve chamber 114a.

The second oil valve chamber 114b receives oil from the first oil valve chamber 114a, and then applies oil pressure to the spring support 122 to be described later, so that the outer rotor 120 and the inner rotor 140 are eccentric. You can change the degree. The eccentric change direction of the outer rotor 120 and the inner rotor 140 by the second oil valve chamber 114b is the same as the first oil valve chamber 114a.

The bypass passage 127 is formed to supply the oil of the first oil valve chamber 114a to the second oil valve chamber 114b.

The bypass passage 127 is formed at one side of the body 110 to supply the oil of the first oil valve chamber 114a to the second oil valve chamber 114b. At this time, the bypass passage 127 is opened and closed by the first and second sealing portions 125a and 125b to be described later, and supply of oil is interrupted.

The outer rotor 120 is formed in a substantially ring shape. The outer rotor 120 is installed in the inner space of the body 110 by a connecting shaft 121 formed on the outer side of the outer rotor 120. The outer rotor 120 is rotated by a predetermined angle with respect to the connecting shaft 121 and eccentrically with the inner rotor 140 to be described later by a predetermined amount. In the inner circumference of the outer rotor 120, a rotary chamber 128 in which vanes 144 and a ring 146, which will be described later, are installed is formed. The rotary chamber 128 is formed in a circular shape and is formed concentrically with the outer rotor 120.

On the outer surface of the outer rotor 120, a spring support portion 122 is formed to protrude.

The spring support part 122 contacts the one end of the support spring 130 to be described later to support the support spring 130. The spring support part 122 is formed in the shape of a rod formed in a predetermined length and width. The spring support part 122 transmits the elastic force of the support spring 130 to the outer rotor 120 so that the outer rotor 120 and the inner rotor 140 are eccentric, and the support spring (120) when the outer rotor 120 is rotated. 130) to be compressed.

The spring support part 122 has an escape prevention end 123 formed at a predetermined height toward the support spring 130 at an end thereof. The release preventing end 123 prevents one end of the support spring 130 from being separated on the spring support part 122 during the low speed operation.

On one side of the outer rotor 120, the oil pressure intermittent portion 124 is disposed toward the first oil valve chamber 114a.

The oil pressure intermittent part 124 supplies the pressure of oil to the second oil valve chamber 114b according to the oil pressure state of the first oil valve chamber 114a.

The oil pressure intermittent portion 124 is formed with an oil flow pipe 126 for allowing oil on the side of the first oil valve chamber 114a to flow to the inlet side of the bypass flow passage 127, and one side thereof has a body 110. Close to the inner one side of the.

In this embodiment, the oil pressure intermittent part 124 is manufactured separately and fixed to the outer surface of the outer rotor 120, but may be integrally formed with the outer rotor 120.

The support spring 130 is installed at one inner side of the body 110, one end is supported by contact with the spring support 122 of the outer rotor 120, and the other end is supported at one inner side of the body 110. Here, the support spring 130 allows the outer rotor 120 and the inner rotor 140, which will be described later, to be eccentric by a predetermined amount by the elastic force of the spring. The amount of oil pumped to each part of the engine is controlled according to the eccentricity of the outer rotor 120 and the inner rotor 140.

Inner rotor 140 is rotatably installed on the inner surface of the body (110). The inner rotor 140 is rotated by receiving a rotational force from the drive shaft of the engine. Inner rotor 140 is formed in a circular shape. The inner rotor 140 may be smaller than the diameter of the rotary chamber 128 and may rotate inside the rotary chamber 128. The rotating shaft connected to the inner rotor 140 is connected to the outside through the body 110. The central axis of the rotary chamber 128 is kept unmoved and is eccentric with respect to the outer rotor 120.

The vanes 144 are slidably coupled radially to the inner rotor 140 and the outer circumferential surface of the inner rotor 140. The vane 144 is used in plurality.

Here, the plurality of vanes 144, the outer end is in contact with the inner circumferential surface of the outer rotor 120 while the inner rotor 140 is rotated out of the radial rotation, the embodiment of the present invention is the outer end of the vane 144 A ring 146 is provided to contact the inner end of the vane 144 so as to be in uniform contact with the inner circumferential surface of the outer rotor 120.

2 is a view showing the configuration of an example of the vortex preventing groove according to the first embodiment of the present invention.

Referring to FIG. 2, a vortex prevention groove 160 is formed on the front and rear surfaces of the body 110 that cover both side surfaces of the outer rotor 120 and the inner rotor 140 from the inside of the body 110.

Vortex prevention groove 160 prevents the vortex of the oil and the resulting cavitation (cavitation) and noise between the both sides of the vane (144) and the inner surface of the body (110) when the oil is pumped by the vanes (144) .

Vortex prevention groove 160 is formed in an arc shape. Vortex prevention groove 160 may be formed in a single piece, it may be formed opposite to both sides with respect to the center of the outer rotor (120). In addition, the vortex preventing groove 160 is preferably formed at a position where both ends of the end of the vane 144 in contact with the inner surface of the outer rotor 120 contact.

The width of both ends of the vortex preventing groove 160 is formed to be narrower than the width of the middle portion. Thus, as shown in Figure 2, the vortex prevention groove 160 is formed such that the width gradually increases from one end to the middle portion, and gradually narrower from the middle portion to the other end. Here, the width of the vortex prevention groove 160 may be the same on both sides with respect to the middle portion. In addition, since the operation degree of the oil pump may vary according to the rotational load of the engine, the amount of change in the width of the vortex preventing groove 160 may not be the same at both ends with respect to the middle part.

The curvature of the outer circumferential side of the vortex preventing groove 160 is formed corresponding to the curvature of the inner circumferential surface of the outer rotor 120. Therefore, the outer circumferential side of the vortex preventing groove 160 may be formed to coincide with the side end of the inner circumferential surface of the outer rotor 120.

In addition, the curvature of the inner circumference of the vortex prevention groove 160 may be variously changed according to the degree of change in the width of the vortex prevention groove 160.

The depth of the vortex prevention groove 160 may be formed in various ways according to the needs of the user. The depth of the vortex prevention groove 160 may be formed to be constant throughout, or may change in response to a change in width.

The present invention configured as described above may operate as follows.

This will be described with reference to FIG. 1 again.

First, when the engine operates, the oil of the oil pan (not shown) flows into the rotary chamber 128 through the suction pipe path (not shown) and is pumped to each friction part of the engine by the vane 144. In detail, the flow of oil in the rotary chamber 128 is first introduced into the body 110, the oil is introduced into the friction portion of the engine through the supply line.

At this time, the inner side of the outer rotor 130 is in communication with the supply line for supplying each frictional part of the engine, by applying pressure to the oil by the vane 144 to feed the oil to each part of the engine.

3 is a sectional view taken along the line A-A of FIG.

1 and 3, it can be seen that the vortex preventing groove 160 is formed between both ends of the vane 144 and the body 110. Here, the vortex prevention groove 160 acts as a flow space of the oil to operate the vane 144 and when the oil is pumped, to prevent the vortex of oil between the vane 144 and the inner surface of the body 110 is generated. do. In addition, the vortex prevention groove 160 is to prevent the generation of cavitation and the noise inside the oil pump.

In the smallest part and the largest part of the distance between the inner circumferential surface of the outer rotor 120 and the outer circumferential surface of the inner rotor 140, the vortex generation degree is relatively smaller than the middle portion, so both ends of the vortex preventing groove 160 are wider than the middle portion. This can be formed small.

The supplied oil is then bypassed and supplied to the first oil valve chamber 114a which is a space between the inner surface of the body 110 and the outer rotor 120.

The pressure of the oil supplied to the first oil valve chamber 114a is applied to the outer rotor 120, and the oil of the first oil valve chamber 114a is formed through the oil flow pipe 126 and the bypass passage 127. 2 After flowing into the oil valve chamber 114b, the pressure of the oil is applied to the spring support 122.

Initially, the outer rotor 120 does not rotate and the inner rotor 142 because the sum of the oil pressures of the first oil valve chamber 114a and the second oil valve chamber 114b is less than the elastic force of the support spring 130. Maintain eccentricity with).

On the other hand, when the oil input to the second oil valve chamber (114b) flows into the support spring 130 side, the pressure is applied to the outer rotor 120 in the opposite direction to the first oil valve chamber (114a) to the oil pump 100 ) Is not smooth, the oil input to the second oil valve chamber 114b side is prevented from flowing to the support spring 130 by the third sealing portion (125c).

Thereafter, the rotation speed of the engine is gradually increased to increase the pressure of the oil flowing into the first oil valve chamber 114a and the increased oil pressure is applied to the outer rotor 120 so that the outer rotor 120 rotates the rotation shaft 121. Rotation with reference, the degree of eccentricity with the inner rotor 142 is reduced.

4 and 5 are views showing the operation of the oil pump according to the first embodiment of the present invention.

Referring to FIG. 4, when the engine speed is gradually increased, the pressure of oil pumped from the rotary chamber 128 to each part of the engine increases, and thus the pressure and oil of the oil supplied to the first oil valve chamber 114a are increased. The pressure of the oil flowing into the second oil valve chamber 114b from the first oil valve chamber 114a through the bypass passage 127 also increases.

When the oil pressure of the first oil valve chamber 114a and the second oil valve chamber 114b is simultaneously applied to the outer rotor 120 and the spring support 122, and the applied pressure is greater than the elastic force of the support spring 130, The pressure is applied to the outer rotor 120 is rotated in a clockwise direction around the rotation shaft 121, the support spring 130 is compressed.

When the outer rotor 120 rotates, the degree of eccentricity with the inner rotor 142 is reduced, so that the increase in the oil supply pressure of the rotary chamber 128 stops at a certain degree.

The compression of the support spring 130 is performed at an engine speed of approximately 1000 rpm from the beginning of the engine operation, and in this state, the inlet of the bypass flow passage 127 is the first sealing portion 125a and the second sealing portion 125b. Located between the oil of the first oil valve chamber 114a may be supplied to the second oil valve chamber 114b.

If the engine speed continues to increase (for example, 1000 rpm or more), the oil pressure of the first oil valve chamber 114a and the second oil valve chamber 114b is increased to increase the amount of rotation of the outer rotor 120.

Referring to FIG. 4 again, the first sealing part 125a and the second sealing part 125b are moved by the rotation of the outer rotor 120 so that the second sealing part 125b is an inlet of the bypass passage 127. It is located on the side and accordingly the bypass flow path 127 is closed to block the oil supply of the second oil valve chamber 114b, so that only the oil pressure of the first oil valve chamber 114a is applied to the outer rotor 120. .

Since only the oil pressure of the first oil valve chamber 114a is applied to the outer rotor 120, the support spring 120 is compressed again and the eccentricity of the outer rotor 120 and the inner rotor 142 is reduced. Here, the compression of the support spring 120 is temporarily caused by the increase in the oil pressure due to the increase in the engine speed.

The oil pressure of the first oil valve chamber 114a applied to the outer rotor 120 increases due to the continuous increase of the engine speed, but the bypass flow path 127 is closed by the second sealing part 125b. Keep it. The width of the second sealing portion 125b is larger than the diameter of the inlet of the bypass passage 127, so that the second sealing portion 125b is within a predetermined range (for example, 1000 to 3000 rpm). The bypass passage 127 remains closed. The width of the second sealing unit 125b may be set in various ways corresponding to the engine speed range according to the needs of the user.

Referring to FIG. 5, after that, when the engine speed is increased to a predetermined level or more, for example, 3000 rpm or more, the pressure of the oil pumped to the rotary chamber 128 is further increased, and the outer rotor in the first oil valve chamber 114a is located. As the pressure applied to the 120 is increased, the outer rotor 120 rotates in a clockwise direction about the rotation shaft 121.

In addition, due to the rotation of the outer rotor 120, the second sealing part 125b is moved to open the inlet of the bypass passage 127 that is closed.

The oil of the first oil valve chamber 114a is transferred to the second oil valve chamber 114b through the bypass channel 127 by opening the bypass channel 127. Thereafter, the oil pressures of the first oil valve chamber 114a and the second oil valve chamber 114b are simultaneously applied to the outer rotor 120, so that the support spring 130 is compressed, so that the outer rotor 120 and the inner rotor are compressed. As the eccentricity of 142 is further reduced than before, the increase in the oil supply pressure of the rotary chamber 128 stops at a certain degree.

Meanwhile, as shown in FIGS. 4 and 5, the intersection of the vortex preventing groove 160 and the outer rotor 120 is reduced by the movement of the outer rotor 120, and thus, through the vortex preventing groove 160. The oil flow rate is also reduced. However, due to the movement of the outer rotor 120, the eccentricity of the outer rotor 120 and the inner rotor 140 is reduced and the rise of the oil supply pressure is also stopped, so that the occurrence of vortex of the oil is also reduced. Thus, even if the intersection of the vortex prevention groove 160 and the outer rotor 120 is reduced, the vortex prevention effect can be continuously obtained.

However, since the shapes of the vortex preventing grooves 160 facing each other may be different from each other, the amount of vortex generation of the oil and the degree of vortex preventing effect thereof may appear differently with respect to the vortex preventing grooves 160 facing each other.

6 is a view showing the pressure state of the oil pump according to the first embodiment of the present invention and the oil pump according to the prior art according to the rotation speed of the engine. In Figure 6, line A1 represents the pressure of the oil pump according to the prior art, line A2 represents the pressure of the oil pump according to the present invention.

7 is a view showing the torque state of the oil pump according to the first embodiment of the present invention and the oil pump according to the prior art according to the rotation speed of the engine. In Fig. 7, line B1 represents the torque of the oil pump according to the prior art, and line B2 represents the torque of the oil pump according to the present invention.

Referring to FIG. 6, in the operation of the oil pump 100, when the rotation speed of the engine is 1000 or less, the pressure of the oil pump 100 in the related art and the present technology is the same. When the engine speed reaches 1000, the pressure of the oil pump 100 gradually increases. However, in the oil pump 100 according to the present invention, the degree of change in the hydraulic pressure is weaker than the oil pump according to the prior art by the prevention of the vortex generation by the vortex prevention groove 160 when the hydraulic pressure rises.

When the rotational speed reaches 3000 or more due to the continuous increase in the engine speed, it can be seen that the pressure of the conventional oil pump and the oil pump according to the present technology are the same.

Referring to FIG. 7, it can be seen that the torque required for the operation of the oil pump is less than 1000 in the conventional oil pump and the oil pump according to the present technology.

When the engine speed is between 1000 and 3000, the oil pressure of the first oil valve chamber 114a is applied to the outer rotor 120, and when the engine speed is 3000 or more, the first oil valve chamber 114a and the second Due to the oil pressure in the oil valve chamber 114b, the eccentricity of the outer rotor 120 and the inner rotor 142 is reduced, so that the pressure inside the oil pump 100 is lowered. At this time, the vortex generation between the vane 144 and the body 110 is also reduced by the vortex prevention groove 160.

When the oil is supplied by the vane 144, the vortex of the oil between the vane 144 and the inner surface of the body 110 is prevented, thereby preventing the vortex, thereby preventing the occurrence of cavitation and noise inside the oil pump. do.

In addition, since the vortex of the supplied oil is prevented so that the flow of oil is made uniform, the oil supply to each engine of the vehicle can be made uniform. In addition, since the oil is supplied uniformly, the generation of noise can be reduced.

8 is a view showing the configuration of an oil pump according to a second embodiment of the present invention.

Referring to FIG. 8, the oil pump according to the second embodiment of the present invention includes a body 110, an outer rotor 220, an inner rotor 140, a support spring 130, a first oil valve chamber 114a, The second oil valve chamber 114b, the bypass passage 127, and the first and second vortex prevention passages 260 and 270 are included.

The same reference numerals are used for the same components as in the previous embodiment, and detailed description thereof will be omitted.

 Since the outer rotor 220 is formed in a form similar to the outer rotor 120 used in the previous embodiment, only the differences will be described.

9 is a perspective view showing the configuration of the outer rotor used in the oil pump according to the second embodiment of the present invention, Figure 10 is a plan view showing the configuration of the outer rotor used in the oil pump according to the second embodiment of the present invention. to be.

9 and 10, a first vortex prevention path 260 acting as an oil flow space on one side of the outer rotor 220 toward the spring support 122 from the rotary chamber 128 of the outer rotor 220. Is formed. In addition, the first vortex prevention passages 260 are formed at both sides of the outer rotor 220.

Accordingly, the first vortex prevention paths 260 are respectively located between the inner walls of the oil pump 200 at both sides of the spring support part 122 side portion of the outer rotor 220.

In addition, a second vortex prevention path 270 is formed at one side of the outer rotor 220 symmetrical to the first vortex prevention path 260 based on the center point of the outer rotor 220.

The second vortex prevention path 270 may be formed in a groove shape on the inner wall side of the rotary chamber 128.

The second vortex preventing passage 270 is formed at both sides of the outer rotor 220. Accordingly, the second vortex preventing passages 270 are respectively located between the inner walls of the oil pump 200 at both sides of the portions opposite to the spring support portion 122 of the outer rotor 220.

The first and second vortex preventing passages 260 and 270 may have the same length on the outer rotor 220, or the length of the second vortex preventing passage 270 may be formed to be shorter than that of the first vortex preventing passage 260. It may be.

The first and second vortex prevention passages 260 and 270 are provided with the vortex of oil and the resulting cavitation between both sides of the outer rotor 220 and the inner surface of the body 110 when oil is pumped by the vanes 144. By preventing cavitation and noise generation, it increases the flow rate and reduces the noise.

At this time, both ends of the first and second vortex prevention passages 260 and 270 are formed with curved surfaces of a predetermined curvature, respectively, to facilitate oil flow. At this time, it is preferable that both ends of the first vortex prevention path 260 are formed to have the same curvature.

In addition, it is preferable that both ends of the second vortex prevention paths 270 formed at positions symmetric to the first vortex prevention path 260 are formed to have the same curvature.

In addition, it is preferable that the end curvature of the first vortex preventing passage 260 and the end curvature of the second vortex preventing passage 270 are the same.

At this time, a tangent b of the inner circumferential surface of the rotary chamber 128 in contact with the tangent a with respect to the end of the first vortex preventing passage 260 and the starting point of the inner space of the outer rotor 220, that is, the end of the vortex preventing passage. ) Preferably forms an angle of 1 ° to 85 °.

Since the curvatures of both ends of the first vortex prevention path 260 are the same, and the ends of the first and second vortex prevention paths 260 and 270 are the same as each other, the curvatures of the first and second vortex prevention paths 260 are The tangent (a) of the end of 270 and the tangent (b) of the inner circumferential surface of the rotary chamber 128 form an angle of 1 ° to 85 °.

11 and 12 are views showing the operation of the oil pump 200 according to the second embodiment of the present invention.

11 and 12, when the engine (not shown) operates, the oil pump 200 is rotated by receiving the rotational force of the engine. In this case, the oil introduced into the body 110 is supplied to each part of the engine through a supply line, and then bypassed to bypass the first oil valve chamber, which is a space between the body 110 and the outer rotor 120. 114a). The pressure of the oil supplied to the first oil valve chamber 114a may be applied to one side of the outer rotor 120 to change the eccentricity of the outer rotor 120 and the inner rotor 140.

As the engine speed increases by a certain amount (for example, 3000 rpm or more), the pressure of the oil pumped to the rotary chamber 128 is further increased, and the pressure applied to the outer rotor 220 from the first oil valve chamber 114a is increased. In other words, the outer rotor 220 rotates in a clockwise direction about the rotation shaft 121.

At this time, since the operation of the components of the oil pump 200 is the same as the previous embodiment, a detailed description thereof will be omitted, and only the differences will be described.

When the outer rotor 220 operates as described above, the oil conveyed by the vanes 144 is one end side of the first vortex prevention path 260 between both sides of the outer rotor 220 and the inner surface of the body 110. After flowing to the rotary chamber 128 side through, and introduced into one end of the second vortex prevention path (270). Subsequently, the fluid flows back to the rotary chamber 128 through the other end of the second vortex prevention path 270 and is discharged through the other end of the first vortex prevention path 260.

In FIG. 11, the arrow indicates the flow of oil.

At this time, the tangent a of one end of the first vortex prevention passage 260 and the tangent b of the rotary chamber 128 in contact with the end form a predetermined angle (1 ° to 85 °) to facilitate the flow of oil. do.

By the first vortex prevention path 260 formed in the outer rotor configured as described above, it is possible to obtain an effect that the oil flow rate is increased by about 30% and the operation noise is reduced by about 10 dB during the operation of the oil pump.

While the present invention has been described with reference to exemplary embodiments, it is to be understood that the invention is not limited to the disclosed embodiments, but, on the contrary, is intended to cover various modifications and equivalent arrangements included within the spirit and scope of the appended claims. Accordingly, the true scope of the present invention should be determined by the technical idea of the appended claims.

100: oil pump
110: body
120, 220: outer rotor
122: spring support
123: exit prevention
124: oil supply intermittent
125: oil flow pipe
126: Bypass Euro
128: rotary room
130: support spring
140: inner rotor
144: vane
146: ring
160: vortex prevention groove
260: first vortex prevention furnace
270: second vortex prevention furnace

Claims (9)

A body having a suction line for sucking oil from an oil pan, and a supply line for supplying the oil introduced from the suction line to each friction part of the engine;
An outer rotor rotatably installed inside the body and having a rotary chamber formed therein;
A plurality of eccentrically installed with respect to the outer rotor and rotated in accordance with the rotation of the drive shaft of the engine and coupled to the outer circumferential surface so as to slidably coupled to one end and the oil feed to the supply line while one end is in contact with the inner circumferential surface of the outer rotor. An inner rotor including a vane;
A support spring having one end in contact with a spring support formed on an outer surface of the outer rotor and the other end in contact with an inner surface of the rotary chamber, for supporting the outer rotor;
A first oil valve chamber formed inside the body and configured to change a position of the outer rotor by applying a pressure of oil supplied from the outside to the outer rotor;
A second oil valve chamber formed inside the body and configured to change a position of the outer rotor by applying a pressure of oil supplied from the first oil valve chamber to the spring support;
A bypass passage for supplying oil from the first oil valve chamber to the second oil valve chamber; And
When the oil is pumped, the oil pump comprising a vortex prevention unit for preventing the vortex of the oil and thereby the cavitation (cavitation) and the noise generated between the inner surface of the body. The method according to claim 1,
The vortex preventing unit includes an vortex preventing groove formed on an inner surface of the body covering the outer rotor and the side of the inner rotor. The method according to claim 2,
The vortex preventing groove is an oil pump formed in an arc shape. The method according to claim 2,
The vortex preventing groove is located in contact with both ends of the vane oil pump. The method according to claim 3,
Both ends of the vortex prevention groove is formed in a narrower than the middle portion of the oil pump. The method according to claim 1,
The vortex preventing portion is formed on one side of the outer rotor toward the spring support side in the rotary chamber of the outer rotor, the first vortex prevention passage formed on both sides of the outer rotor and
A second vortex prevention path formed at a position symmetrical to the first vortex prevention path on the outer rotor with respect to the center point of the rotary chamber;
Oil pump comprising a. The method of claim 6,
An oil pump formed in a groove shape on the inner wall side of the rotary chamber of the second vortex preventing passage. The method of claim 6,
Both ends of the first and second vortex preventing passages are formed in a curved shape of the same curvature. The method according to claim 8,
The tangent of the end of the first and second vortex preventing passage and the tangent of the inner circumferential surface of the rotary chamber in contact with the starting point of the end is formed with an angle difference of 1 ° to 85 °.

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