JPH07259751A - Improvement regarding pump - Google Patents

Abstract

PURPOSE: To prevent excessive fatigue of oil by arranging a changeover valve on one of outlets for immediately returning oil from a corresponding pump for the supplement of high supplement ratio and pressure, and arranging a supply part driving shaft which is connected to independent paired pumps having a common inlet, and is not connected to an outlet. CONSTITUTION: A driving shaft 10 penetrates rotors of two rotor pumps 12, 14 and is fixed in its angle. A common suctioning passage 16 is connected to both pumps. A passage 24 receives pressure from an outlet 18 which is then applied to a control valve 28 pushed to a closure position by means of a spring 30. At the closure position, a ball valve 32 of a flow passage is opened, and fluid is flowed from the flow passage 22 to an outlet 20 through the flow passage 26. When pressure is increased in the flow passage 18 and exceeds foce of the spring 30, the valve 28 is moved to open the flow passage 22 directly communicated with an oil reservoir. The ball valve is returned to an original position since bidirectional flow between the flow passages 18 and 22 is eliminated.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION The present invention relates to I.S. C. It relates to the oil pump of the engine. Such pumps are engine driven and the pump output is nominally proportional to engine speed.

[0002]

2. Description of the Related Art In the context of engines, hydraulic demand curves are usually not proportional to engine speed. An amount of oil that exceeds the oil required to maintain the bearing pressure is sent to the oil receiver via the mechanism of the control valve. Otherwise, there will be excessive pressure that can result in engine damage. This extra oil is a waste of energy. Many proposals have been made, such as using a gerotor pump to address this problem by changing the eccentricity of the shaft to reduce the output at high speeds. The aim of the present invention is to provide a new solution to this old problem.

According to the present invention, the engine oil pump is equipped with a switching valve at one of the outlets which has the effect of returning the oil directly from the corresponding pump in order to supply at a high oil supply ratio / pressure, and a common inlet supply It consists of a feed section drive shaft that is connected to an independent set of pumps having a section, but not to the outlet.

According to a preferred embodiment of the present invention, engine oil is connected to a set of gerotor oil pumps having an inlet connected to a common supply and an outlet connected to a common oil flow passage. The control valve, which consists of a drive shaft and is provided between the outlet and the oil supply passage, is arranged so that the oil is directed from the gerotor set to the common supply when the valve is open. It is arranged to open automatically at pressure / high refueling ratio.

The valve may be a simple spring control valve. If the pump output pressure is low, the valve will remain closed and all output will go to the refueling flow path. When the pressure rises mainly due to the engine speed, which may be due to the decrease in viscosity such as in the case of low temperature, the valve opens, and a part of the output of one gerotor set, and eventually all of the oil supply flow. It is set to bypass the path and return directly to the source, for example a sump.

The power efficiency of the jet rotor set depends on the discharge pressure. Therefore, by connecting the outlet directly to the oil sump, the pressure is effectively zero, which alleviates the pump workload and minimizes the energy consumed by the gerotor set in question at such times. .

A gerotor pump, as is well understood in the art, consists of a rotor with n male lobes housed in an annulus with n + 1 female lobes. This forms a series of chambers between the rotor and the annulus, each of which is joined to the plane of the pump body perpendicular to the axis of rotation and to the line of contact between the parts. Even if the rotor and ring rotate at different speeds, the chamber rotates about an axis (the rotor and ring are parallel but not identical to the axis) and change size. The chamber grows from a minimum where there is one lobe between two lobes on one part to a maximum at the opposite diameter point by half a turn, and the chamber grows. As it grows, it moves above the suction port. When it continues to rotate again, the chamber becomes smaller and moves above the discharge port leading to the oil supply passage.

[0008]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT The attached schematic diagram shows a preferred device, FIG. 1 showing full flow, ie in both pump operating positions, and FIG. 2 showing one pump operating low flow condition. In the figure, the drive shaft 10
Are angle-invariant through the rotors of the two gerotor pumps indicated by the reference numerals 12, 14. The common suction channel 16 is connected to both pumps. The discharge flow path from the pump 12 is connected to, for example, an oil supply flow path 20 leading to the main oil path of the engine.

With the pair of connecting flow passages 24 and 26 extending from the flow passage 22 to the flow passage 18, the discharge flow passage 22 from the pump 14 is connected to the oil receiver which is the same supply source as that of the suction 16. Extend.

The flow path 24 receives the pressure from the outlet 18,
It acts on the control valve 28 which is spring propelled at 30 to the closed position shown in FIG. In this closed position, the ball valve 32 of the flow passage 26 is open and can flow through the flow passage 26 from the flow passage 22 to the outlet 20. Both channels have the effect of sending oil to the engine and both pumps absorb energy.

If the pressure exceeds the spring 30 when the pressure rises in the flow passage 18, the valve 28 moves to open the passage of the flow passage 22 which goes straight to the oil receiver, and the ball valve also passes the flow passages 18 and 22. There is no bi-directional flow between the two, and one pump is in place to refuel the engine and the other engine returns to the sump.

[0012]

[Brief description of drawings]

FIG. 1 is a diagram of a preferred device in a full flow condition with both pumps in the operating position.

FIG. 2 is a diagram of the preferred device in a low flow state with one pump in the actuated position.

[Explanation of symbols]

 10 Drive Shafts 12 and 14 Gerotor Pump 16 Common Suction Flow Path 18 Outlet 20 Oil Supply Flow Path 22 Discharge Flow Path 26 Flow Path

Claims (4)

[Claims] 1. A set of pumps driven by a common drive shaft, wherein a common suction supply section and a lubrication oil flow passage are avoided unless the valve is in the closed position, and the corresponding pump is directly connected to the supply section. An engine oil pump, characterized in that it has a connected but independent outlet flow path with a switching valve at one of the outlets which has the effect of returning oil. 2. A drive shaft connected to a set of gerotor oil pumps having an inlet connected to a common supply source, and pump outlets connected to a common oil supply passage, one outlet, An engine oil pump, wherein a control valve is mounted between an oil supply passage configured to send oil directly from one of the gerotor sets to a common supply when the valve is opened. 3. A pump according to claim 2, characterized in that the valve is arranged in the discharge line from one of the pumps and is activated by the pressure in the discharge line of the other pump. 4. A discharge line of one pump is connected to an oil supply line, a discharge line of another pump is connected to a suction source or a line, and one set of flow lines is two lines. 4. The pump according to claim 2, wherein one of the pipe lines includes a switching valve operated by pressure of the other pipe line, and the other includes a ball check valve. .