WO2018092930A1

WO2018092930A1 - Oil pump control valve

Info

Publication number: WO2018092930A1
Application number: PCT/KR2016/013229
Authority: WO
Inventors: 이창훈; 문국찬; 박지훈; 정영진
Original assignee: 주식회사 유니크
Priority date: 2016-11-16
Filing date: 2016-11-16
Publication date: 2018-05-24

Abstract

The present invention relates to an oil pump control valve enabling expansion of a control section and reduction of loss due to a discharge port by means of gradually increasing or decreasing the flow rate of an oil discharged through a control port and/or the discharge port during the movement of a spool. The present invention comprises: a valve for controlling the inlet and outlet of an oil; and a solenoid for driving the valve. The valve comprises: a pipe-shaped holder having the discharge port on the upper end, the control port on the middle end and a supply port on the lower end; and the spool having a first land and a second land, which come in contact with the inner peripheral side of the holder, on the upper end and the lower end, respectively, and having a driving groove between the first land and second land. A first notch groove, which connects the control port and discharge port, is formed on the upper end of the first land. A second notch groove, which connects the supply port and control port, is formed on the lower end of the first land. The first notch groove is in a tapered shape which gradually becomes wider upward. And the second notch groove is in a tapered shape which gradually becomes wider downward.

Description

Oil pump control valve

The present invention relates to a valve for controlling the flow rate of the oil supplied to the oil pump, more specifically, the discharge port by gradually increasing or decreasing the flow rate of the oil discharged through the control port and / and the discharge port during the movement of the spool It is an oil pump control valve which can reduce the loss through and extend the control section.

The oil pump sucks oil stored in an oil pan and drives the oil pump to each part of the engine when the engine is driven. The oil pressurized by the oil pump is applied to the friction causing part to reduce the frictional resistance and prevent the wear of the part.

In general, the pressure and flow rate of the oil discharged from the oil pump is proportional to the revolutions per minute (rpm) of the engine. For example, a large amount of high pressure oil is pumped in a high speed driving section where the engine speed is high. However, when oil is supplied in a large amount, the resistance due to the viscosity of the oil is increased and power performance and fuel economy are deteriorated.

Recently, a variable oil pump, in which a pumping volume is changed by a slider rotating around a pivot, is used to maintain a constant oil pressure and flow rate regardless of the engine rotation speed. The variable oil pump can reduce the pump load and reduce fuel consumption in the high speed operation section by changing the pumping volume and adjusting the oil pressure and flow rate.

Meanwhile, the variable oil pump includes a pair of chambers in which oil is supplied so that the slider can rotate about the pivot, and an oil pump control valve for controlling oil supplied to the pair of chambers.

Looking at the conventional oil pump control valve with reference to Figure 9, the holder 10, the spool 20 installed inside the upper end of the holder 10, the adjusting screw 30 coupled to the upper end of the holder 10 and , A spring 40 interposed between the spool 20 and the adjusting screw 30, a case 40 surrounding the lower end of the holder 10, a bobbin 50 installed inside the case 40, and a bobbin. The coil 60 wound around the outer circumferential surface of the 50, the plunger 70 installed inside the lower end of the holder 10, the cover 92 coupled to the lower end of the case 80, and the side surface of the case 80. It consists of a protruding connector 94.

The upper outer peripheral surface of the holder 10 is provided with a supply port 12 for supplying oil and a control port 14 for discharging the oil controlled at a predetermined pressure, and the control screw 30 through the control port 14. A discharge port 32 for discharging the introduced oil to the outside is formed. In addition, a first land 22 and a second land 24 are formed at an upper end and a lower end of the spool 20, and an operating groove 26 is formed between the first land 22 and the second land 24. do.

In the oil pump control valve having the above-described configuration, when the spool 20 rises, the supply port 12 and the control port 14 are connected by the first land 22, and the oil supplied through the supply port 12 is provided. It is discharged to a chamber (not shown) via this control port 14. On the other hand, when the spool 20 rises, the control port 14 and the discharge port 32 are connected by the first land 22 so that oil introduced through the control port 14 passes through the discharge port 32. Drained to an oil pan (not shown).

By the way, since the spool 20 is raised to connect the control port 14 and the supply port 12 at the initial stage, the control port 14 and the discharge port 32 are not blocked but remain connected to each other. Most of the oil transferred to the control port 14 in 12) is discharged to the oil pan (not shown) through the discharge port 32 (see FIG. 10). That is, the amount of oil flowing into the oil pump (not shown) through the control port 14 is insufficient. Therefore, the load of the oil pump increases and causes a problem of lowering fuel economy.

The present invention is to solve the above-mentioned problems of the prior art, by gradually increasing or decreasing the flow rate of the oil discharged through the control port or / and the discharge port when moving the spool to reduce the loss through the discharge port and control The purpose is to provide an oil pump control valve that can extend the section.

An oil pump control valve according to the present invention for achieving the above object includes a valve for regulating the entry and exit of oil, and a solenoid for operating the valve. The valve has a pipe-shaped holder having a discharge port formed at an upper end, a control port formed at an interruption thereof, and a supply port formed at a lower end thereof, and a first land and a second land contacting the inner circumferential surface of the holder at an upper end and a lower end, respectively. And a spool which is formed and an operating groove is formed between the first land and the second land.

A first notch groove for connecting the control port and the discharge port is formed at an upper end of the first land, and a second notch groove for connecting the supply port and the control port is formed at a lower end of the first land. In this case, the first notch groove has a tapered shape in which the width thereof is extended toward the upper portion, and the second notch groove has a tapered shape in which the width thereof is expanded toward the lower portion thereof.

According to the present invention configured as described above, the first notch groove connecting the control port and the discharge port, the second notch groove connecting the supply port and the control port has a shape that extends toward the end of the first land, the spool When this rises or falls, the flow rate (or pressure) of oil discharged through the control port and / or the discharge port gradually increases or decreases. Therefore, it is possible to linearly control the change in the flow rate (or pressure) according to the increase or decrease of the current, and because the slope of the current-flow rate (or pressure) graph rises slowly, the control section can be extended. In particular, when the spool rises, the first notch groove is gradually closed, thereby reducing the loss of oil through the discharge port, thereby reducing the load of the oil pump and improving fuel economy.

1 is a cross-sectional view of an oil pump control valve according to an embodiment of the present invention.

2 is a view showing a spool of the oil pump control valve according to an embodiment of the present invention.

Figure 3 is an enlarged view of the notch groove of the oil pump control valve according to an embodiment of the present invention.

4 and 6 are views showing the operation of the oil pump control valve according to an embodiment of the present invention.

7 and 8 is a performance graph of the oil pump control valve according to an embodiment of the present invention.

9 and 10 are views of the oil pump control valve according to the prior art.

With reference to the accompanying drawings will be described embodiments of the present invention; In the following description of embodiments according to the present invention, and in adding reference numerals to the components of each drawing, the same reference numerals are added to the same components as much as possible even though they are shown in different drawings.

As shown in FIG. 1, an oil pump control valve according to an exemplary embodiment of the present invention includes a valve 100 for controlling oil in and out, and a solenoid 200 for operating the valve 100.

The valve 100 is positioned on a flow path of an oil pump housing (not shown) to selectively supply oil transferred from an oil pan (not shown) to the chamber (not shown). Looking at the configuration, the holder 110, the spool 120 is installed to be movable inside the holder 110, the adjusting screw 130 coupled to the upper portion of the spool 120, the spool 120 and the adjustment It includes a spring 140 interposed between the screw 130.

The holder 110 has a pipe shape extending from the valve 100 to the solenoid 200. The upper part of the holder 110 (the upper part based on the flange 110c) is a part which controls and discharges the pressure of the oil supplied to the valve 100, and the lower part of the holder 110 is a magnetic field for operating the valve 100. This is the part that induces. Hereinafter, the upper portion of the holder 110 will be referred to as the hydraulic portion 110a and the lower portion of the holder 110 will be referred to as the magnetic portion 110b.

The hydraulic part 110a has a pipe shape having an outer diameter larger than that of the magnetic part 110b. A supply port 112 for supplying oil is formed at a lower end of the hydraulic part 110a, and a control port 114 for discharging oil controlled at a predetermined pressure is formed at the hydraulic part 110a. In addition, an O-ring 116 is installed on the lower outer circumferential surface of the hydraulic unit 110a to prevent leakage of oil.

The adjusting screw 130 is provided at the upper end of the hydraulic unit 110a, and the spring 140 is installed at the lower portion of the adjusting screw 130. The adjusting screw 130 is for controlling the moving distance and the moving speed of the spool 120 by adjusting the elasticity of the spring 140 supporting the spool 120. The adjusting screw 130 is screwed to the top of the hydraulic portion (110a) to finely adjust the elasticity of the spring (140).

The adjustment screw 130 is formed with a discharge port 132. The discharge port 132 is a port for discharging a portion of the oil introduced from the supply port 112 and the oil introduced from the control port 114 to an outside, that is, an oil pan (not shown). At this time, the discharge port 132 is formed at a position (outside of the spring 140) a predetermined distance from the center of the adjustment screw 130, and consists of four radially disposed relative to the center of the adjustment screw 130. .

As shown in FIG. 9, when the discharge port 32 is located at the center of the adjusting screw 30, that is, inside the spring 40, the oil is discharged through the discharge port 32 when the spring 40 is compressed. Will interfere. On the other hand, since the discharge port 132 of the present embodiment is located outside the spring 140, it can exclude the interference by the spring 140 in the discharge process of the oil. Therefore, the oil can be smoothly discharged through the discharge port 132, the discharge port 132 is composed of four radially arranged can be more smoothly discharged oil. In particular, the structure through which the spring 140 is inserted into the upper end of the spool 120 may discharge the oil more effectively.

The magnetic part 110b has a pipe shape having an outer diameter smaller than that of the hydraulic part 110a. A magnetic induction groove 118 is formed on the outer peripheral surface of the magnetic part 110b, and an O-ring 116 is installed on the lower outer peripheral surface to prevent leakage of oil.

Magnetic induction groove 118 is a means for securing a sufficient magnetic force to effectively control the high pressure and high flow oil. As shown in FIG. 1, the stopping wall surface of the magnetic part 110b in which the magnetic induction grooves 118 are formed is formed to be thinner than the upper and lower portions thereof. The magnetic field generated from the coil 230 when the power is applied is induced along the magnetic part 110b but is concentrated in the magnetic induction groove 118 having a relatively thin thickness.

The magnetic induction groove 118 described above uses the principle that the magnetic flux density increases as the area of the object on which the magnetic field is formed decreases. In particular, the magnetic induction groove 118 of the present embodiment has a tapered shape, the thickness of which becomes thinner toward the center, and thus can concentrate the magnetic field more effectively. Therefore, it is possible to precisely control the plunger 240 moving by the magnetic field, through which it is possible to control the high pressure and high flow oil.

The spool 120 is a means for selectively connecting the supply port 112, the control port 114, the discharge port 132 during its movement. The spool 120 has a rod shape having a plurality of stages having different outer diameters, and is installed to be movable in the hydraulic part 110a.

1 to 3, the shape of the spool 120 will be described in more detail.

The spool 120 has a rod shape extending in the longitudinal direction of the holder 110. The first land 122 and the second land 124 are formed at the upper end and the lower end of the spool 120, and the operation groove 126, which is a small diameter part, is formed at the stop. In addition, a flow path 128 connecting the discharge port 132 and the magnetic part 110b is formed in the spool 120.

The first land 122 and the second land 124 contact the inner circumferential surface of the holder 110 to guide the movement of the spool 120. In particular, the first land 122 contacts the upper or lower portion of the control port 114 when the spool 120 moves to block the connection of the

ports

112, 114, and 132. For example, when the spool 120 rises, the supply port 112 and the control port 114 are connected, and the connection between the control port 114 and the discharge port 132 is blocked (see FIG. 6). In addition, when the spool 120 is lowered, the connection of the supply port 112 and the control port 114 is blocked, and the control port 114 and the discharge port 132 are connected.

Meanwhile,

notch grooves

122a and 122b are formed in the first land 122 according to the present embodiment to gradually increase or block the connection of the

ports

112, 114 and 132. The

notch grooves

122a and 122b may include a first notch groove 122a disposed radially along the upper circumference of the first land 122 and a second radially disposed along the lower circumference of the first land 122. It consists of a notch groove 122b.

The first notch groove 122a and the second notch groove 122b have a tapered shape that extends toward the end portion so that the opening between the holder 110 and the first land 122 may be gradually opened when the spool 120 moves. Have That is, the first notch groove 122a has a semi-conical shape that extends toward the top, and the second notch groove 122b has a semi-cone shape that extends toward the bottom.

The ratio of the volume of the 1st notch groove 122a and the 2nd notch groove 122b is as follows (refer FIG. 3).

The length (L ₁₎ when the provisions of 1.5 d, a first notched groove (122a): The first notched groove (122a) thickness (W ₁₎ and the second one a thickness (W ₂₎ the ratio of the notch groove (122b) of And the thickness W ₂ ratio of the second notch groove 122b is 1:15, and the height H ₁ of the height of the first notch groove 122a and the thickness W ₂ of the second notch groove 122b are: 1: 6.

In addition, the ratio of the length L ₂ of the second notched groove 122b and the thickness W _{2 of} the second notched groove 122b is 1:10, and the height H ₂ of the second notched groove 122b is The thickness W ₂ ratio of the second notch grooves 122b is 1: 6.

The spool 120 including the

notch grooves

122a and 122b having the above-described shape has an overlap section in which both the first notch grooves 122a and the second notch grooves 122b are opened. That is, there is a section in which the control port 124 is connected to both the supply port 122 and the control port 124 by the

notch grooves

122a and 122b.

In this overlap section, since a part of the oil transferred from the supply port 112 to the control port 114 is discharged to the outside through the discharge port 132, the pressure (or flow rate) of the oil transferred through the control port 114 ) Can be prevented from rapidly changing. Therefore, it is possible to linearly control the change in pressure according to the increase or decrease of the current for moving the spool 120. In addition, since the slope of the current-pressure graph gradually rises, the control section can be extended (see FIG. 7). In particular, since the first notch groove 122a is gradually closed as the spool 120 rises, the discharge of oil through the discharge port 132, that is, the loss of oil, may be reduced (see FIG. 8).

Referring to FIG. 1 again, the solenoid 200 includes a case 210 surrounding the magnetic part 11b, a bobbin 220 installed inside the case 210, and a coil wound around the outer circumferential surface of the bobbin 220. 230, a plunger 240 installed inside the magnetic part 11b, a cover 250 coupled to the other end of the case 210, and a connector 260 protruding to the side of the case 210. .

The case 210 has a cup shape in which a lower surface is opened and the upper surface is closed. An accommodation space 212 is formed inside the case 210, and a bobbin 220 is installed in the storage space 212. The lower end of the case 210 is curled to surround the cover 250. When curling the lower end of the case 210, the bobbin 220 and the cover 250 is pressed to the flange 116 side, it is possible to prevent the flow of parts installed in the case 210, the case 210 It is possible to prevent foreign matter from entering the lower portion of the.

Bobbin 220 is a hollow spool shape. The coil 230 is wound around the outer circumferential surface of the bobbin 220. The magnetic field generated from the coil 230 when the power is applied is induced by the magnetic part 110b and the case 210 to raise the plunger 240. At this time, the strength of the magnetic field is proportional to the strength of the current flowing along the coil 230 and the number of coils 230 wound on the bobbin 220. Therefore, since a strong magnetic field is generated as a strong current is applied to the coil 230 or the coil 230 is wound much, the movement of the plunger 240 can be reliably controlled.

The plunger 240 is a movable iron core reciprocating by the magnetic field generated by the coil 230, is installed to be movable in the magnetic part 110b, and is in contact with the lower end of the spool 120.

The plunger 240 is formed with a passage 242 penetrating the plunger 240 up and down. When the plunger 240 reciprocates, the passage 242 has oil filled in the upper portion of the plunger 240 to the lower portion of the plunger 240 and oil filled in the lower portion of the plunger 240 is the plunger 240. Is transported to the top of the. At this time, the passage 242 is eccentric a predetermined distance from the center of the plunger 240, to prevent the passage 242 is closed by the contact with the spool 120.

The lower end of the plunger 240 is formed into a curved surface to make local surface contact with the bottom of the cover 250. When the plunger 240 and the cover 250 is in contact with the local surface, the plunger 240 can be smoothly raised by blocking the flow of the magnetic field which was directly led to the plunger 240 through the cover 250. In addition, even if the bottom of the cover 250 is slightly inclined, the frictional resistance due to the inclination of the plunger 240 may be eliminated without affecting the inclination of the plunger 240.

The surface of the plunger 240 is electroless nickel plated. In addition, the inner circumferential surface of the holder 110, in particular, the inner circumferential surface of the magnetic portion 110b in contact with the plunger 240 is softened. As described above, when the plunger 240 is plated and the magnetic portion 110b is soft nitrided, friction generated when the plunger 240 is moved may be reduced.

The connector 260 is a means for applying power to the coil 230. A plurality of terminals 262 are installed inside the connector 260. The connector 260 protrudes outward through the side of the case 210.

The operation of the valve will be described with reference to FIGS. 4 to 6.

4 is a state in which power is not applied to the solenoid 200 of FIG. 1. At this time, since the spool 120 is elastically supported by the elasticity of the spring 140, the spool 120 is lowered to the bottom dead center. The first land 122 of the spool 120 is in contact with the lower portion of the control port 114 to block the connection of the supply port 112 and the control port 114 and at the same time control port 114 and the discharge port 132 ) Allows the connection.

FIG. 5 is an initial state in which power is applied to the solenoid 200 (in FIG. 1), which is the overlap state described above. The spool 120 is raised to a certain height so that the first land 122 is spaced apart from both the upper and lower portions of the control port 114. In this case, the supply port 112 is connected to the control port 114 through the second notch groove 122b, and the control port 114 is connected to the discharge port 132 through the first notch groove 122a. Therefore, a part of the oil transferred from the supply port 112 to the control port 114 is discharged to the outside through the discharge port (132).

FIG. 6 is a state in which the maximum oil is applied to the solenoid 200 (200), and the spool 120 is raised to the top dead center. The first land 122 of the spool 120 is in contact with the upper portion of the control port 114 to block the connection of the control port 114 and the discharge port 132 and at the same time supply port 112 and the control port 114 ) Allows the connection. Therefore, the total amount of oil transferred from the supply port 112 to the control port 114 is pumped through the control port 114.

While the present invention has been described through the preferred embodiments, the above-described embodiments are merely illustrative of the technical idea of the present invention, and various changes may be made without departing from the technical idea of the present invention. Those of ordinary skill will understand. Therefore, the protection scope of the present invention should be interpreted not by the specific embodiments, but by the matters described in the claims, and all technical ideas within the equivalent scope should be interpreted as being included in the scope of the present invention.

Claims

An oil pump control valve comprising a valve for intercepting oil in and out, and a solenoid for operating the valve.

The valve,

A discharge port is formed at an upper end, a control port is formed at an interruption, and a pipe-shaped holder formed at a lower end of the supply port;

A spool having a first land and a second land contacting the inner circumferential surface of the holder at upper and lower ends, respectively, and an operation groove formed between the first land and the second land;

An oil pump control valve comprising a notch groove formed in at least one of an upper end of the first land and a lower end of the first land.
The method according to claim 1,

The notch groove may include a first notch groove formed at an upper end of the first land and connecting the control port and the discharge port, and formed at a lower end of the first land to connect the supply port and the control port. An oil pump control valve comprising two notches.
The method according to claim 2,

The first notch groove has a tapered shape that extends toward the upper portion, the second notched groove has a tapered shape that extends toward the lower portion of the oil pump control valve.
The method according to claim 3,

The first notch groove and the second notch groove is an oil pump control valve, characterized in that the semi-conical shape corresponding to each other.
The method according to claim 4,

And the first notch groove and the second notch groove are radially disposed along the circumference of the first land.
The method according to claim 3,

When specified La 1.5: the thickness (W 1) of the first notched groove (122a) and a first thickness (W 2) the ratio of the two notched grooves (122b)

The ratio of the length L 1 of the first notch groove 122a to the thickness W 2 of the second notch groove 122b is 1:15, and the height H 1 of the first notch groove 122a and the second are not. The thickness (W 2 ) ratio of the notch grooves 122b is 1: 6,

The ratio of the length L 2 of the second notch groove 122b to the thickness W 2 of the second notch groove 122b is 1:10, and the height H 2 of the second notch groove 122b and the second are not. Oil pump control valve, characterized in that the thickness (W 2 ) ratio of the notch groove (122b) is 1: 6.
The method according to any one of claims 1 to 6,

Oil pump control valve, characterized in that there is an overlap (overlap) section in which both the first notch groove and the second notch groove open when the spool moves.
The method according to any one of claims 1 to 6,

A control screw coupled to the top of the holder; And

Further comprising a spring interposed between the spool and the adjusting screw,

The oil pump control valve, characterized in that the discharge port is formed in the adjusting screw.
The method according to claim 8,

The discharge port is an oil pump control valve, characterized in that located outside the spring.
The method according to claim 9,

The discharge port is an oil pump control valve, characterized in that consisting of a plurality of radially disposed relative to the center of the adjusting screw.