KR20200071528A - Binary Damping Section Type Oil Pump - Google Patents

Abstract

An oil pump (1) with dual damping sections of the present invention maintains a fluid damping effect in a variable relief valve (10) generating first and second bypass flow rates with an upper damping flow path (28) having a constant fluid filling state, so that an increase in the required pressure/flow rate of an engine lubrication system in line with a trend of engine performance improvement eliminates instability of behavior of the variable relief valve (10), thereby further improving valve behavior.

Description

Binary Damping Section Type Oil Pump}

The present invention relates to an oil pump, and in particular, to a damping section dual-type oil pump suitable for the required pressure/flow rate of the engine lubrication system required by the engine high performance trend.

In general, an engine lubrication system applied to a vehicle engine allows the oil pumped by an oil pump to circulate inside the engine at a lubricating oil flow rate, thereby promoting the normal operation of the engine lubrication parts composed of various bearing elements and hydraulic operating parts in the engine.

In particular, the oil pump is operated as a variable oil pump by incorporating a variable flow rate system that controls an excessively high pressure of the discharge flow rate into a bypass flow rate inside the oil pump. For example, the variable flow system has a variable relief valve, and the variable relief valve is a valve operating oil, a bypass channel (or relief channel), an oil channel divided into a damping channel, and a plunger-type valve that generates valve displacement in the channel , It includes a spring supporting the valve.

Therefore, in the oil pump to which the variable relief valve is applied, the pressure is applied to the valve with the valve operating flow path, so that the valve is displaced downward (in mm), and the bypass flow path (or the oil pump discharge flow rate returns to the suction side again due to valve displacement) Relief flow path) prevents the flow rate/pressure supplied to the engine from becoming excessively high by reducing the final discharge flow rate from the oil pump as it occurs, and the drain hole through which the oil is supplied from the suction side is always drilled by the damping flow path. By connecting to the suction side flow path, the oil always stays at the rear end of the valve, and the oil acts as a fluid damping.

Therefore, the variable relief valve of the oil pump is an oil pump driven torque by the number of revolutions of the engine and the associated rotor speed. When the discharge flow rate increases, the accompanying high pressure lowers the oil pump to such an extent that it does not adversely affect the engine lubrication parts. The disadvantage of fuel efficiency due to excessively high pressure may be eliminated.

Domestic Publication Patent 10-2002-0021060 (2002.03.18)

However, in order for the engine lubrication system to meet the required pressure/flow increase for high-performance engines, oil pumps also require high-performance, and oil pump performance increases due to the structural characteristics of the oil pump, which increases engine speed and increases rotor speed. It requires high operational stability for variable relief valves.

The reason for this is that the oil pump generates variable displacement by generating valve displacement instability due to the valve resonance phenomenon caused by the spring and the fluid damping force due to the oil dropping in the damping flow path along with the amplitude component of the valve displacement under the condition of the fixed rotational speed of the rotor during oil discharge. This is because the operation stability of the valve is impaired.

For example, the valve displacement instability is generated by the pressure of the pulsating component that destabilizes the displacement of the valve, and is further promoted by a sudden pressure change around the valve formed at the moment of bypass, which increases the displacement of the valve abnormally. The valve resonance phenomenon is caused by a spring supporting the valve resonating at a specific frequency.

In particular, the drop in the fluid damping force is due to the oil exiting to the suction side through the natural gravity discharge action in the space at the rear end of the valve when the oil pump is stopped for a long period of time. It is a major cause of instability in valve behavior, but it is a cause of various noises by amplifying it. This phenomenon is bound to be a fundamental limitation of the damping structure method using the suction-side oil hole like the existing structure.

Therefore, in order to improve the vibration, noise, and performance aspects of the variable oil pump, it is very important to improve the operational stability of the variable relief valve by improving the abnormal displacement due to instability/resonance/fluid damping of the valve displacement.

Moreover, in recent years, the tendency to develop a high-performance engine that is getting more severe is to increase the required pressure/flow rate of the lubrication system to increase the oil pump capacity, thereby reducing the performance of the oil pump and adversely affecting the entire lubrication system. The need to improve behavioral instability is becoming more important.

In view of the above, the present invention solves the valve displacement instability and the valve resonance phenomenon by improving the fluid damping effect of the dual damping flow path, thereby improving the behavioral instability of the variable relief valve, thereby requiring the engine lubrication system to meet the engine performance trend. A damping section that is easy to increase pressure/flow rate, and in particular, because the oil is always present in the valve operating flow path for valve displacement, the valve behavior can be further improved by forming an additional fluid damping effect by the oil even during low/high pressure bypass operation. The purpose is to provide a dual type oil pump.

In order to achieve the above object, the oil pump of the present invention fills the front end section and the rear end section of the valve, which is operated in the valve operating flow path connected to the first bypass flow path and the second bypass flow path, which lowers the discharge flow pressure with the oil flow rate. A variable relief valve supported by a damping flow path and allowing the oil flow rate to continue a fluid damping action on the valve; Characterized in that it is included.

As a preferred embodiment, the damping flow path is formed in the front end section and is sealed in the stroke region of the valve so as to be separated from the secondary bypass flow path, and is formed in the rear end section and the primary low pressure bypass flow path. It is divided into a lower damping flow path sealed by the valve so as to be separated.

In a preferred embodiment, the upper damping flow path introduces the oil into the upper damping oil path leading from the discharge flow path to the upper damping flow path. The lower damping flow channel flows the oil from the discharge flow path to the lower damping oil path leading to the lower damping flow path.

In a preferred embodiment, the lower damping flow path is sealed with a plug in which a spring for supporting the valve is built-in.

In a preferred embodiment, the valve is placed on the valve operating flow path to form a stroke communicating the primary bypass flow path and the secondary bypass flow path, and is integrally formed with the valve body to seal the shear section It consists of a top end and a bottom end integrally formed with the valve body to seal the rear end section.

In a preferred embodiment, the valve body and the upper end lead to the upper narrow body and are integrated, and the upper narrow body forms a path through which the oil introduced from the secondary bypass flow path is discharged. The valve body and the lower end are connected to the lower narrow body to be integrated, and the lower narrow body forms a path through which oil introduced from the primary bypass flow path is discharged.

In a preferred embodiment, the variable relief valve is built in a valve housing, and the valve housing is formed on one side of a pump housing in which an intake flow passage and a discharge flow passage communicate with the valve. The suction passage is a passage through which the oil flows from the outside into the interior space of the pump housing, and the discharge passage is a passage through which the oil exits the pump housing.

The oil pump of the present invention implements the following operations and effects with a dual structure of the damping section.

First, by improving the fluid damping performance of the oil pump, the stability of the behavior of the variable relief valve is secured by resolving the instability of the valve displacement of the variable relief valve. Second, since the oil is always present in the valve operating flow path for valve displacement, the valve behavior can be further improved due to the additional fluid damping effect by the oil even in the second stage bypass operation. Third, the oil pressure can satisfy the required pressure/flow increase of the engine lubrication system, which is required by the engine high-performance trend, by the stable behavior of the variable relief valve. Fourth, the valve resonance phenomenon, which may occur suddenly, can be stably handled while excellent in noise and vibration aspects of the valve due to stable valve behavior. Fifth, by generating a fluid damping effect in a constant oil filling section in which gravity discharge is suppressed at the front and rear parts of the valve, an oil pump noise problem occurring at start-up after long-term engine standing can be solved.

1 is a configuration diagram of a damping section dualization type oil pump according to the present invention, and FIG. 2 is a detailed configuration diagram of a variable relief valve and oil passage applied to the damping section dualization type oil pump according to the present invention, and FIG. 3 is the present invention The limiting example of the displacement design of the variable relief valve according to the configuration, Figure 4 is a fluid damping action state of the variable relief valve during the operation of the oil pump according to the present invention, Figure 5 is an experimental example of the fluid damping effect according to the present invention.

Hereinafter, exemplary embodiments of the present invention will be described in detail with reference to the accompanying exemplary drawings, and as such examples, those skilled in the art to which the present invention pertains may be embodied in various different forms, and thus are described herein. It is not limited to the embodiment.

Referring to FIG. 1, the oil pump 1 is a valve housing 20 forming one side of the pump housing 3, and 1 of the bypass flow passage 23 linked to an increase in discharge flow rate/pressure according to an increase in rotor rotation speed, A variable relief valve (10) that acts to lower the excessively high discharge pressure at the secondary bypass flow rate is incorporated. In particular, the valve housing 20 is provided with a damping flow path 27 toward the upper/lower side of the variable relief valve 10, and the damping flow path 27 continues the fluid damping action when the variable relief valve 10 is operated. All of the valve displacement instability/resonance/fluid damping force that impairs valve operation stability is eliminated.

Accordingly, the oil pump 1 is characterized by a damping section dualization type oil pump in which the damping passage 27 provided upward/lower of the variable relief valve 10 continues the fluid damping action.

Specifically, the pump housing (3) forms the overall shape of the oil pump (1), the rotor assembly (5) consists of a rotor and vanes to pump and discharge the oil through the rotor rotation, the suction passage (7-1) Forms a passage through which oil flows into the interior space of the pump housing 3 from the outside, and the discharge passage 7-2 forms a passage through which oil is discharged from the interior space of the pump housing 3 to the outside.

Therefore, the pump housing 3, the rotor assembly 5 and the suction/discharge passages 7-1, 7-2 are the same as the components of a conventional oil pump. However, the pump housing 3 has a difference that forms a damping flow path 27 in the valve housing 20 in which the variable relief valve 10 is accommodated.

Specifically, the variable relief valve 10 includes a valve housing 20, a valve operating channel 21, a bypass channel 23, ports 25 and 26, a damping channel 27, a valve 30, and a plug ( 40) and a spring 50 (see FIG. 2). Particularly, the damping flow path 27 maintains the fluid damping effect when the oil is bypassed from the discharge flow path 7-2 to the suction flow path 7-1, while improving the instability of the behavior of the valve 30 while matching the engine performance trend. When the required pressure/flow rate of the engine lubrication system is increased, the oil pump discharge flow rate pressure is lowered without adversely affecting the engine lubrication parts.

For example, the valve housing 20 is integrally formed with the pump housing 3 on the side surface of the pump housing 3 and is used as a place where the flow paths 21, 23, 25, 26, 27 are formed.

For example, the valve operating flow path 21 is provided as a stroke forming space of the valve 30, a bypass flow path 23 and a damping flow path 27 are formed, and ports 25 and 26 are pierced to prevent oil outflow. Is done.

For example, the bypass flow path 23 is connected to the discharge flow path 7-2 of the pump housing 3, and then flows through the valve operating flow path 21 to the suction flow path 7-1 to discharge the flow path 7-2. And a flow path through which the flow rate is bypassed between the intake passage 7-1. To this end, the bypass flow path 23 is divided into a relatively low pressure primary bypass flow path 23-1 and a relatively high pressure secondary bypass flow path 23-2. The primary bypass flow path 23-1 is located toward the lower damping flow path 29 of the damping flow path 27, and the primary bypass port 25 of the inflow/outflow ports 25A, 25B for oil flow/outflow ), the secondary bypass flow path 23-2 is located toward the upper damping flow path 28 of the damping flow path 27, and the secondary flow of the inflow/outflow ports 26A and 26B for oil flow/outflow. A bypass port 26 is provided.

Therefore, the primary bypass flow path 23-1 flows into the bypass flow rate of the discharge path 7-2 through the inlet port 25A of the primary bypass port 25 to inhale the flow path from the discharge port 25B. By exporting to (7-1), the oil pressure going to the discharge passage (7-2) is lowered. In addition, the secondary bypass flow path 23-2 is a discharge path (7) to the inlet port 26A of the secondary bypass port 26 when forming a higher pressure than the primary bypass flow path 23-1 -2) Bypass the flow rate of the inlet to be discharged from the discharge port (26B) to the suction flow path (7-1) to lower the oil pressure to the discharge flow path (7-2). Therefore, the first and second bypass flow passages 23-1 and 23-2 lower the oil pump discharge flow pressure by two-step adjustment.

For example, the damping flow path 27 is a lower end of the valve 30, the upper damping flow path 28, located in the valve front end section (or the left end section) of the valve operating flow path 21 to act on the upper end of the valve 30 It is divided into a lower damping flow path 29 located in the valve rear end section (or the right end section) of the valve operating flow path 21 to act on. In this case, the upper damping flow path 28 is supplied with a flow rate through the upper damping oil path 28A, and the lower damping flow path 29 is supplied with a flow rate through the lower damping oil path 29A, thereby providing an oil supply path. It is formed independently.

For example, the valve 30 forms a stroke in the valve operating flow path 21 at a high pressure flow rate bypassed from the discharge flow path 7-2, followed by the primary bypass flow path 23-1 according to the pressure. Relief pressure to the suction flow path 7-1 is formed through the secondary bypass flow path 23-2. Particularly, the valve 30 simultaneously receives a fluid damping action due to a flow rate filled in the lower damping passage 29 and a fluid damping action due to a flow rate filled in the upper damping passage 28.

For example, the plug 40 closes the lower damping flow path 29. The spring 50 is located in the space of the lower damping flow path 29 to support the valve 30 by bullet.

2, a detailed structure of the valve 30 is illustrated. As shown, the valve 30 is formed of a rod bar shape forming a valve stroke in the length of the valve operating flow path 21, the valve body 31, the upper narrow body 32, the upper end 33, the lower end It is divided into a narrow body 34 and a lower end 35.

For example, the valve body 31, the upper end 33 and the lower end 35 are made of the same diameter, and the upper narrow body 32 and the lower narrow body 34 are relatively small in diameter. Is done.

Therefore, the valve body 31 is positioned as a valve operating flow path 21, and the upper end 33 is positioned toward the upper damping flow path 28 to be separated from the secondary bypass flow path 23-2. 28), and the lower end 35 is located toward the lower damping flow path 29 to seal the lower damping flow path 29 so as to be separated from the primary bypass flow path 23-1. The body 32 acts such that a relatively high pressure is discharged through the secondary bypass flow path 23-2 to the suction flow path 7-1, and the lower narrow body 34 has a relatively low high pressure primary. It acts to be discharged through the bypass flow path 23-1 to the suction flow path 7-1.

Meanwhile, FIG. 3 illustrates the setting relationship between the stroke of the valve 30 and the upper damping flow passage 28.

Figure 3 (a) is a valve standard stroke (A), which is the upper damping flow path 28, the upper end damping oil continued from the discharge flow path 7-2 in a closed state with the upper end 33 of the valve 30 It represents a state in which the damping flow rate is filled through the path 28A and thus does not escape to the secondary bypass flow path 23-2. In addition, the lower damping flow path 29 is filled with the damping flow rate through the lower damping oil path 29A continued from the discharge flow path 7-2 in a closed state with the lower end 35 of the valve 30 to the valve stroke. The flow-out caused by this is prevented.

Therefore, in the stroke behavior of the valve 30 according to the valve standard stroke (A), the upper damping flow path 28 and the secondary bypass flow path 23-2 due to the upper end 33 of the valve 30 The fluid damping effect can be maintained without being communicated, and the fluid damping effect is maintained without being communicated with the primary bypass flow path 23-1 while the lower damping flow path 29 is supported by the spring 50. Can be.

On the other hand, Fig. 3(B) is a valve overstroke (B), which is the upper damping flow path 28, which is closed at the upper end 33 of the valve 30, while the upper damping continues at the discharge flow path 7-2. Although the damping flow rate is filled through the oil path 28A, the upper end 33 of the valve 30 due to the relatively high high pressure is excessively lowered, indicating a state connected to the secondary bypass flow path 23-2.

Therefore, in the stroke behavior of the valve 30 according to the valve over-stroke B, the upper damping flow path 28 and the secondary bypass flow path 23-2 are caused by the upper end 33 of the valve 30. Since it is in communication, it is inevitable to lose the fluid damping effect.

From this, the valve operating flow path 21 of the variable relief valve 10, the bypass flow path 23, the damping flow path 27, the valve body 31, the upper/lower narrow body 32,34, the upper/lower end It can be seen that the ends 33 and 35 should be designed in accordance with the valve standard stroke A of FIG. 3(a).

Meanwhile, FIGS. 4 and 5 are operating states and performance diagrams of the oil pump 1 to which the variable relief valve 10 designed with the valve standard stroke A is applied.

Referring to FIG. 4, the oil pump 1 discharges oil into the oil pump drive torque by the rotor speed interlocked with the engine speed in a valve initial state (A) where the oil is completely empty inside the pump housing 3. When this is increased, the high pressure accompanying it generates displacement of the variable relief valve 10 with time, and proceeds to the valve charging state (B). Therefore, in the valve filling state (B), the high pressure of the discharge flow path 7-2 through the primary bypass flow path 23-1 or the secondary bypass flow path 23-2 is applied to the bypass oil. It is in the state of exiting towards -1).

However, the valve damping maintaining state (C) is the valve standard stroke (A), so that the upper end 33 of the valve 30 blocks the upper damping passage 28 in the valve filling state (B), thereby preventing the secondary bypass passage 23- By not communicating with 2), the valve 30 can receive the fluid damping action of the flow rate filled in the upper damping passage 28 as it is.

Referring to FIG. 5, the fluid relief is maintained in the upper damping channel 28 while the variable relief valve 10 proceeds from the primary bypass channel 23-1 to the secondary bypass channel 23-2. As a result, it is proved by the analysis result or the experimental result that the stable side of the valve behavior is maintained by almost disappearing the oil variability of the valve 30.

As described above, the damping section according to the present embodiment, the dualization type oil pump 1 is a variable relief valve 10 that generates first and second bypass flows into the upper damping flow passage 28 having a constant fluid filling state. By continuously maintaining the fluid damping effect, the required pressure/flow rate increase of the engine lubrication system in line with the tendency to increase the engine performance is eliminated, and the instability of the behavior of the variable relief valve 10 is eliminated, thereby further improving the valve behavior.

1: Oil pump 3: Pump housing
5: rotor assembly 7-1: suction flow path
7-2: Discharge flow path
10: variable relief valve 20: valve housing
21: valve operating passage 23: bypass passage
23-1: 1st Bypass Euro 23-2: 2nd Bypass Euro
25: primary bypass port 25A, 26A: inlet port
25B, 26B: Outlet port 26: Secondary bypass port
27: damping flow path 28: upper damping flow path
28A: Upper damping oil path 29: Lower damping flow path
29A: Bottom damping oil path 30: Valve
31: valve body 32: upper narrow body
33: upper end 34: lower narrow body
35: bottom end 40: plug
50: spring

Claims (14)

A damping flow path filled with an oil flow rate supports a front end section and a rear end section of a valve operated in a valve operating flow path connected to a primary bypass flow path and a secondary bypass flow path to lower the discharge flow rate pressure, and the oil flow rate is applied to the valve. A variable relief valve that sustains the fluid damping action against the;
Oil pump comprising a.
The oil pump according to claim 1, wherein the damping channel is divided into an upper damping channel formed in the front end section and a lower damping channel formed in the rear end section.
The oil pump according to claim 2, wherein the upper damping flow path is closed with the valve so as to be separated from the secondary bypass flow path.
The oil pump according to claim 3, wherein the sealing of the upper damping passage is made in a stroke region of the valve.
The oil pump according to claim 2, wherein the upper damping flow path includes an upper damping oil path through which the oil flows.
The oil pump according to claim 5, wherein the upper damping oil path extends from the discharge passage) to the upper damping passage.
The oil pump according to claim 2, wherein the lower damping flow path is closed with the valve so as to be separated from the primary bypass flow path.
The oil pump according to claim 7, wherein the lower damping flow path extends from the discharge flow path to the lower damping flow path.
The oil pump according to claim 7, wherein the lower damping flow path is sealed with a plug in a state in which a spring supporting the valve is built-in.
The method according to claim 1, The valve is placed on the valve operating flow path and the valve body forming a stroke communicating the primary bypass flow path and the secondary bypass flow path, integrally formed on the valve body to seal the shear section An oil pump comprising an upper end and a lower end integrally formed with the valve body to seal the rear end section.
The oil pump according to claim 10, wherein the valve body and the upper end lead to the upper narrow body and are integrated, and the upper narrow body forms the secondary bypass flow path.
The oil pump according to claim 10, wherein the valve body and the lower end are connected to the lower narrow body to be integrated, and the lower narrow body forms the primary bypass flow path.
The oil pump according to claim 1, wherein the variable relief valve is built in a valve housing, and the valve housing is formed on one side of a pump housing in which an intake flow passage and a discharge flow passage communicate with the valve.
The oil pump according to claim 13, wherein the suction passage is a passage through which the oil flows from the outside into the interior space of the pump housing, and the discharge passage is a passage through which the oil exits the pump housing.

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