JPH0596478U - Vane type oil pump - Google Patents

Abstract

(57) [Abstract] [Purpose] The purpose of the present invention is to use an oil passage that communicates with the line pressure regulating valve for the oil passage configuration for setting the groove width in a continuously variable transmission or to bypass the line pressure regulating valve. When adopting the structure of oil supply to the lubricating pressure regulating valve by using the oil passage of the structure, lack of lubricating oil at low rotation speed, delay of rise of line pressure due to oil supply to lubricating pressure circuit, and power It is to obtain a hydraulic control mechanism having an oil passage structure that can prevent loss. [Constitution] The present invention uses an oil pump as a so-called balanced type base.
Oil pumps 1D1 and 1D2 which are composed of a pump and communicate with the high pressure chambers 1C1 and 1C2 of the vane pump 1.
Is provided and at least two line pressure adjusting valves 2 and lubricating pressure adjusting valves 3 are independently connected to the oil discharge port.

Description

[Detailed description of the device]

[0001]

[Industrial applications]

 The present invention relates to a vane type oil pump.

[0002]

[Prior Art]

 A so-called continuously variable transmission mechanism has a structure in which a belt is stretched between a pair of pulleys, and the groove width of the pulleys on which the belts are hung is changed so that the drive side and the driven side have the same width. There is a structure for changing the obtained gear ratio. By the way, as one of the mechanisms for changing the groove width of the pulley described above, a movable conical plate opposed to one fixed conical plate constituting the pulley is displaced axially by using a hydraulic mechanism. There is a structure that allows it. As an example of the hydraulic mechanism described above, for example, an oil pump and a line pressure regulating valve are connected by an oil passage, and the line pressure regulating valve sets a predetermined pressure to discharge the oil to be discharged from the movable conical plate. Some have been designed to lead to a hydraulic circuit for displacement control.

By the way, in the above-mentioned hydraulic mechanism, excess oil may be circulated for lubrication in the line pressure regulating valve. In this case, the structure is the line pressure regulating valve described above. A lubricating oil discharge port is provided in the pressure valve, and a lubrication circuit is connected to this port, or it is connected between the line pressure regulating valve and the movable conical disc displacement control hydraulic circuit described above. There is a structure in which a bypass oil passage leading to the lubrication circuit is connected to the existing oil passage.

[0004]

[Problems to be solved by the device]

 However, in the above hydraulic control structure, when trying to obtain a high line pressure when the discharge rate of the oil pump is low at a low engine speed, the surplus oil used for lubrication is used in the former lubrication structure. There was a problem that lubrication oil became insufficient due to almost no oil discharge, and each sliding part in the continuously variable transmission was worn or seized. Also, in the latter lubrication structure, since the lubrication oil is taken from the oil passage where the line pressure is set, the line pressure does not rise to the set value, and the clamping force of the belt by the displacement control of the movable conical plate is increased. Since the setting cannot be done easily, there were problems such as belt slippage and poor response for setting the gear ratio.

Therefore, in order to solve such a problem, it may be possible to use an oil pump having a large theoretical discharge amount. However, in this case, the engine output is reduced by driving the pump, that is, so-called pump loss increases. As a result, power performance will be deteriorated and fuel consumption will be adversely affected. In addition, when the line pressure is reduced to a high pressure and used for lubrication as described above, the difference in the pressure set for the line pressure is greater than when the pressure for lubrication is set directly. The power of the oil pump will increase. In other words, the amount of time spent for setting the line pressure is reduced by this pressure and becomes a loss for the driving efficiency of the oil pump.

In view of the above-mentioned problems in the conventional hydraulic control mechanism, an object of the present invention is to provide a vane type oil pump having a structure capable of favorably supplying oil while suppressing power loss of the oil pump. It is in.

[0007]

[Means for Solving the Problems]

 To achieve this object, the present invention is provided with at least two or more rotors driven by a prime mover, a cam ring facing the outer peripheral surface of the rotor, and at least two locations between the rotor outer peripheral surface and the cam ring inner wall surface. It is characterized in that it has a pump chamber and a discharge port formed for each pump chamber, and that the discharge port is connected to oil passages having different required hydraulic pressures.

[0008]

According to the present invention, since the plurality of oil discharge ports provided in the vane pump are independently connected to the line pressure regulating valve and the lubricating pressure regulating valve, the line pressure is lowered. A stable hydraulic pressure can be obtained.

[0009]

【Example】

 1 to 4, the details of the embodiment of the present invention will be described below.

1 and 2 are schematic diagrams for explaining the principle of the vane type oil pump according to the embodiment of the present invention. That is, the above-described oil pump 1 is configured by a so-called balanced vane pump, and the vane 1A1 included in the rotor 1A is used as the inner surface of the cam ring 1B that houses the rotor 1A. -It is configured such that at least two or more positions that can be contracted toward the center of rotation by the rotation of the motor 1A can be configured as a pump chamber. In Fig. 1, the pump chambers can be provided at two positions. A cocoon shape is shown, and FIG. 2 shows a triangular shape in which the pump chambers can be provided at three locations. The high-pressure chambers 1C1 and 1C2 forming the discharge part of the pump chamber described above are located on the side where the volume of the space partitioned by the vane 1A1 gradually decreases as the rotor 1A rotates in the direction of the arrow in the figure. Therefore, when passing through the high pressure chambers 1C1 and 1C2, the vane 1A1 lifts in the direction of contracting toward the center of the rotor 1A. In the high pressure chambers 1C1 and 1C2, as the rotor 1A rotates, the volume of the space partitioned by the vanes 1A1 gradually decreases, so that the internal oil is discharged using the increase in pressure obtained. It has become.

For this reason, the high pressure chambers 1C1 and 1C2 are provided with oil discharge ports 1D1 and 1D2, and of these oil discharge ports, the inner surface shape of the cam ring 1B shown in FIG. The reference numeral 1D1 is connected to the oil passage 2A leading to the line pressure regulating valve 2 as shown in FIG. 3, and the reference numeral 1D2 is connected to the oil passage 3A leading to the lubricating pressure regulating valve 3 in FIG. It is connected. In FIG. 3, reference numeral 4 indicates a drain passage of excess oil from the line pressure regulating valve 2 and the lubricating pressure regulating valve 3.

On the other hand, in FIG. 1, on the side where the volume of the space partitioned by the vane 1A1 at the position facing the high pressure chambers 1C1 and 1C2 gradually increases in accordance with the rotation of the rotor 1A, a negative portion forming a suction portion in the pump chamber is formed. A pressure chamber 1E is provided. Therefore, when passing through the negative pressure chamber, the vane 1A1 is lifted in the direction in which it extends toward the outside of the rotor 1A. Then, in the negative pressure chamber 1E, the oil is sucked inward by the negative pressure generated when the volume of the space partitioned by the vanes 1A1 gradually increases as the rotor 1A rotates. It has become so. Therefore, the negative pressure chamber 1E is provided with an oil suction port 1Ea, and the oil is introduced into the negative pressure chamber 1E through the oil suction port 1Ea. Therefore, according to the rotation of the rotor 1A, when the vane 1A1 passes through the negative pressure chamber 1E, oil is sucked into the negative pressure chamber 1E from the oil suction port 1Ea, and the sucked oil has the vane 1A1 in the high pressure chambers 1C1 and 1C2. Is discharged toward the line pressure regulating valve 2 and the lubricating pressure regulating valve 3 via the oil discharge ports 1D 1 and 1D2.

Since the present embodiment has the above-described structure, in FIG. 3, the oil in the oil pan is cleaned of impurities through the strainer 5 and then rotated according to the rotation of the rotor 1A. 1 is sucked into the negative pressure chamber 1E, and is discharged from the high pressure chambers 1C1 and 1C2 toward the pressure regulating valves 2 and 3 through the oil discharge port 1D.

On the other hand, in the example shown in FIG. 1 and FIG. 3, the oil and the discharge port 1D were provided at two places with the rotation center of the rotor 1A interposed therebetween. As shown in Fig. 3, an oil passage connection diagram when the pump chambers obtained by the inner surface shape of the cam ring 1B are set at three locations (the pump chambers having the high pressure chambers indicated by the symbols 1C1, 1C2, 1C3 in Fig. 2) It is shown. In this case, among the high pressure chambers, the high pressure chamber 1C1 has an oil passage 2A leading to the line pressure regulating valve 2, and the high pressure chamber 1C2 has an oil passage 3A leading to the lubricating pressure regulating valve 3. The high pressure chamber 1C3 is connected to, for example, an oil passage 6A leading to a control pressure regulating valve 6 for setting a reference pressure for controlling each pressure regulating valve by operating a solenoid valve (not shown). According to the configuration described above, it is possible to prevent the amount of discharge to each oil discharge port from being reduced even if the size of the oil pump is not greatly increased by one oil pump.

[0015]

[Effect of the device]

As described above, according to the present invention, an oil pump is constituted by a vane pump capable of forming a high pressure chamber by a rotor rotating inside a cam ring, and an oil discharge port is provided in the high pressure chamber obtained by the shape of the cum ring in the oil pump. It is possible to provide an independent oil passage for the line pressure regulating valve and the lubricating pressure regulating valve, and to apply the uniform pressure generated in each high pressure chamber by the oil pump to each hydraulic device and the lubrication part as it is. Therefore, it is possible to prevent a shortage of lubricating oil due to a change in line pressure. Further, since the line pressure does not drop when the lubricating oil is supplied, it is possible to prevent deterioration of the response of the belt clamping pressure in the continuously variable transmission mechanism.

Further, according to the present invention, since the line pressure regulating valve and the lubricating pressure regulating valve are connected to the oil pump through independent oil passages, a lubricating pressure lower than the line pressure is independently set. As a result, it is possible to prevent waste of the pump output used for setting the line pressure, and to reduce the occurrence of power loss. Further, even when one pump is used, the required pressure can be obtained without using a large structure to obtain a high output.

[Brief description of drawings]

FIG. 1 is a model diagram for explaining the principle structure of an oil pump used in a hydraulic control mechanism according to an embodiment of the present invention.

FIG. 2 is a model view for explaining a modified structure of the oil pump shown in FIG.

3 is a hydraulic circuit diagram for explaining a hydraulic control mechanism using the oil pump shown in FIG.

FIG. 4 is a hydraulic circuit diagram for explaining another configuration of a hydraulic control mechanism using the oil pump shown in FIG.

[Explanation of symbols]

 1 oil pump 1A rotor 1A1 vane 1B cam ring 1C1, 1C2, 1C3 high pressure chamber 1D oil outlet 2 line pressure regulator 2A oil passage 3 lubrication pressure regulator 3A oil passage 6 control pressure regulator 6A oil passage

Claims (1)

[Scope of utility model registration request] 1. A rotor driven by a prime mover, a cam ring facing the rotor outer peripheral surface, a pump chamber formed at least at two or more points between the rotor outer peripheral surface and the cam ring inner wall surface, and the pump chamber. A vane type oil pump, characterized in that it has a discharge port formed for each, and the discharge port is connected to oil passages having different required hydraulic pressures.