JPH0322498Y2 - - Google Patents

Description

[Detailed description of the invention] (a) Technical field of the invention The present invention relates to a lubrication circuit for an internal combustion engine.

(b) Background of the technology Since an internal combustion engine has many rotating and sliding parts that require oil supply, as a means to efficiently supply oil to these parts, branching the oil to each member has been developed. A concentrated main gear rally is provided, and oil is force-fed to the main gear rally from an oil pan using an oil pump.

FIG. 7 shows the general structure of a lubrication circuit for an internal combustion engine equipped with such means. The oil 4 is delivered to the main gear rally 2 via a bypass oil filter 5, an oil cooler 6, a full flow oil filter 7, and shot valves 8 and 9. Since this circuit uses a gear type oil pump 3, a safety valve 10 is provided, and a regulator valve 11 is provided to maintain the oil pressure in the main gear rally 2 constant. It is being

The driving horsepower consumed for the operation of such a circuit is mainly the driving force of the oil pump 3, but
The driving force of the oil pump 3 also acts on the oil 4 that is returned from the regulator valve 11 to the oil pan 1, resulting in a loss of energy.

Therefore, it is desired to reduce the driving horsepower consumption in the lubrication circuit of the internal combustion engine.

(c) Prior Art and Problems As a means for reducing the consumed drive horsepower in the lubrication circuit of an internal combustion engine, it is known that, for example, as shown in FIG. 8, the regulator valve 11 is provided close to the oil pump 3. (“Hino Technical Report No. 32”)
(See pages 32 to 37, published in August 1981).

This conventional example was developed with a focus on the delivery pressure of the oil pump 3, but although the pressure loss in the oil cooler 6 etc. was taken into consideration, the increase in pressure loss due to clogging due to use and the temperature of the oil 4 There is a problem in that sufficient consideration is not given to the conditions (ie, the viscosity of the oil 4), and it may not be possible to maintain the oil pressure in the main gear rally 2 well. Furthermore, the amount of oil delivered by the oil pump 3 is not considered at all, and there is a problem in that drive horsepower is unnecessarily consumed for the flow rate of the oil 4 that is returned from the regulator valve 11 to the oil pan 1. .

As a solution to the above problem,
Oil pump drive device for an internal combustion engine disclosed in Publication No. 83613 (Utility Application No. 164983) and Japanese Patent Application Publication No. 164983
A variable displacement vane pump shown in Japanese Patent No. 48-52004 has been proposed.

However, since the former drives the oil pump via a fluid coupling, it has the disadvantage of poor transmission efficiency of driving force.

In addition, since the distribution valve (control means) that controls the delivery amount (discharge amount) is provided separately, it is large and unsuitable for installation in a narrow space such as an internal combustion engine for an automobile. Appropriate.

The latter uses a handle to turn a gear to control the delivery amount, so the delivery amount is approximately constant.
Not suitable for automobiles that accelerate or decelerate.

(d) Purpose of the invention The present invention has been made in view of the above, and its purpose is to improve the transmission efficiency of driving force and to make the control of the delivery amount suitable for use in automobiles that accelerate and decelerate. An object of the present invention is to provide a lubrication circuit for an internal combustion engine that is optimal for a device disposed in a narrow space such as an internal combustion engine.

(E) Structure of the invention In order to achieve this object, the lubrication circuit for an internal combustion engine according to the invention is an internal combustion engine in which oil is force-fed to the main gear lary by an oil pump installed between the oil pan and the main gear lary. In this lubrication circuit, the oil pump is a trochoid pump, and the trochoid pump has a pinion that meshes with a ring gear, a rack that meshes with the pinion, a plunger provided at one end of the rack, and a spring provided at the other end of the rack. is incorporated in a storage chamber, and the storage chamber has a pressure chamber between it and the plunger, and a pressure hole communicates with the pressure chamber to control the control means for controlling the delivery amount in response to the oil pressure of the main gear rally. It is integrated into the trochoid pump.

(F) Embodiments of the invention Hereinafter, embodiments of the lubrication circuit for an internal combustion engine according to the invention will be described.

FIG. 1 shows the entire lubricating circuit for an internal combustion engine according to the present invention, and the drawing is characterized by the omission of the safety valve 10 and regulator valve 11 in the conventional example described above. The oil pump 3 used here is a trochoid pump, and between the oil pump 3 of this trochoid pump and the main gear rally 2, there is a control that makes the delivery amount of the oil pump 3 respond to the oil pressure of the main gear rally 2. Means 12 are associated.

The fact that the delivery amount of the oil pump 3 is made to respond to the oil pressure of the main gear rally 2 by the control means 12 eliminates the unnecessary flow rate of the oil 4 and reduces the consumed drive horsepower. This means that the oil pressure will also be kept constant.

The oil pump 3 is an improved version of the trochoid pump as shown in FIGS. 2 and 3, and the outer rotors 3b and 3b', which are eccentrically provided on the inner rotor 3a, are divided into two parts in the axial direction. It has a structure in which ring gears 3c and 3c', which are similarly divided into two, are provided on the outer periphery of the rotor 3', eccentrically relative to the outer rotor 3b and concentrically relative to the inner rotor 3a. These inner rotor 3a, outer rotor 3
b, 3b', ring gears 3c, 3c' are the casing 3
d, and the ring gears 3c, 3
C' meshes with a pinion 12a which is a part of the control means 12 built in the lower part of the casing 3d.

Control means 1 linked to this oil pump 3
2 is a pinion 12 other than the pinion 12a.
Rack 12b meshing with a and rack 12b
The pump includes a plunger 12c provided at one end of the rack 12b and a spring 12d provided at the other end of the rack 12b. The storage chamber 3e has a pressure chamber 3e' between it and the plunger 12c, and the pressure chamber 3e' has a pressure hole 3e.
This pressure hole 3e'' is connected to a communication pipe (not shown) that communicates with the main gear rally 2.
is connected, and the oil 4 in the main gear gallery 2 is pressurized into the pressure chamber 3e' to operate the control means 12.

In the state shown in FIGS. 2 and 3, the control means 12
2, the rack 12b and plunger 12c are moved toward the right in FIG. 2 by the bias of the spring 12d. When the shaft 3g is rotated by the drive gear 3f in this state, the inner rotor 3a that is axially aligned with the shaft 3g rotates, and the pump chamber 3h formed by the inner rotor 3a and the outer rotors 3b and 3b' is moved due to the misalignment between the two. The operation of a normal trochoid pump is performed in which the oil 4 is expanded and contracted by the suction port 3i and is discharged from the delivery port 3j.

When oil pressure acts on the pressure chamber 3e', the plunger 12c is pressed and the spring 1
2d and press the rack 12b against the pinion 1.
Rotate 2a. The rotating pinion 12a is
As shown in FIG. 4, one ring gear 3c in mesh is rotated in one direction. Although not shown, the other ring gear 3c' is rotated in the opposite direction to the one ring gear 3c. This ring gear 3
Since the rotational outer peripheries of casings 3c and 3c' are restricted by the casing 3d, deviations occur on the inner peripheries as shown. This shift causes the phases of the outer rotors 3b, 3b' to differ with respect to the inner rotor 3aZ, as shown in FIG. 5, causing contraction of the pump chamber 3h, in other words, the amount of oil 4 delivered decreases. Moreover, this difference in phase causes the expansion and contraction of the pump chamber 3h between the outer rotors 3b, 3b' and the inner rotor 3a to be delayed in time, so that some of the oil 4 is The oil 4 is recovered to the suction port 3i without being discharged to the delivery port 3j, further promoting a reduction in the amount of oil 4 delivered.

When the oil pressure to the pressure chamber 3e' is released, the state shown in FIGS. 2 and 3 is restored. However, the structure of the control means 12 means that the mutual change between the states shown in FIGS. 2 and 3 and the states shown in FIGS. 4 to 6 is not performed stepwise but gradually. It is clear from the above that there is no risk of a sudden change in delivery amount having an adverse effect on each part of the circuit.

For the oil pump 3 consisting of the trochoid pump described above, it is also possible to replace the control means 12 with a suitable actuator and to operate the actuator by linking the oil pressure of the main gear rally 2 with an electrical signal.

(g) Effects of the invention As described above, the present invention uses a trochoid pump as an oil pump, a pinion that meshes with the ring gear of the trochoid pump, a rack that meshes with the pinion, and a plunger provided at one end of the rack. A spring provided at the other end of the rack is incorporated into a storage chamber, and the storage chamber has a pressure chamber between it and the plunger, and a pressure hole communicates with the pressure chamber to control the amount of oil delivered to the main gear rally. By integrally providing the pressure-responsive control means in the trochoid pump, the driving force can be directly transmitted to the trochoid pump without going through a fluid coupling, so that the efficiency of driving force transmission can be improved. Furthermore, since the delivery amount is controlled manually or automatically by the control means, it is suitable for use in automobiles that accelerate or decelerate control of the delivery amount. Moreover,
Since the trochoid pump and the control means are integrated, it is compact and is therefore ideal for installation in extremely narrow spaces such as internal combustion engines for automobiles.

[Brief explanation of the drawing]

Fig. 1 is a circuit diagram showing an embodiment of a lubrication circuit for an internal combustion engine according to the present invention, Figs. 2 to 6 show structural examples of an oil pump used in the present invention, and Fig. 2 is a sectional view. , FIG. 3 is a sectional view taken along the line -- in FIG. 2, FIGS. 4 to 6 are sectional views of main parts in the operating state, FIG. FIG. 2 is a circuit diagram showing a conventional example. DESCRIPTION OF SYMBOLS 1... Oil pan, 2... Main gear rally, 3... Oil pump, 4... Oil, 12... Control means.

Claims (1)

[Scope of utility model registration request] In a lubrication circuit for an internal combustion engine in which an oil pump provided between an oil pan and a main gear rally pumps oil to the main gear rally, the oil pump is a trochoid pump, and a pinion meshes with a ring gear of the trochoid pump; A rack that meshes with the pinion, a plunger provided at one end of the rack, and a spring provided at the other end of the rack are incorporated into a storage chamber, and the storage chamber has a pressure chamber between it and the plunger, A lubrication circuit for an internal combustion engine, characterized in that the trochoid pump is integrally provided with a control means that has a pressure hole communicating with the pressure chamber and controls the delivery amount in response to the oil pressure of the main gear rally.