JPH09256969A - Oil pump device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To suppress unnecessary operation to an oil amount or more which is necessitated in an internal combustion engine side, and reduce driving horse power so as to feed operating oil efficiently. SOLUTION: A plurality of suction ports 31 are arranged to correspond to enlarged side spaces 22g to 22i, 22k in each space group formed in a pump chamber 10, and the operating condition of an oil pump 1 is switched and controlled by a control valve 7 into a first condition in which a plurality of intake ports 31 are communicated with each other and suction operation is carried out in the enlarged side spaces 22g to 22i, 22k, and a second condition in which operating oil is forcibly fed from the discharge port 33 of a supplying passage 5 either one of a plurality of intake ports 31 and suction operation is eliminated in a part of the enlarged side spaces 22g to 22i, 22k.

Description

Detailed Description of the Invention

[0001]

TECHNICAL FIELD The present invention relates to an oil pump device. INDUSTRIAL APPLICABILITY The present invention can be applied to an oil pump device having a characteristic that the hydraulic pressure increases as the rotational speed of the crankshaft of the internal combustion engine of the vehicle increases.

[0002]

2. Description of the Related Art In an oil pump device, as the number of rotations of a rotor increases, the amount of hydraulic oil discharged from a discharge port increases, so that the oil pressure generated by the oil pump device increases. By the way, conventionally, there is known an oil pump device in which two gear pumps are integrally provided (Japanese Utility Model Laid-Open No. 61-23485). In this type, in a low-speed rotation region where the hydraulic pressure tends to be low, two gear pumps are driven to secure the discharge amount of the hydraulic oil, thereby securing the required hydraulic pressure. On the other hand, in the high-speed rotation region, the discharge amount increases and the hydraulic pressure can be expected to increase. Therefore, only one gear pump is driven to avoid excessive hydraulic pressure and improve work efficiency.

Further, as shown in FIG. 9, a relief valve 3 has been conventionally used.
An oil pump device equipped with 00 is also known. In this case, a pump body 100 having a suction port 101 and a discharge port 102, a rotor 200 having a large number of teeth rotatably arranged in a pump chamber 105 of the pump body 100, and a hydraulic fluid from the discharge port 102 A relief valve 300 that operates in response to hydraulic pressure.

In this case as well, the rotor 2 is used as described above.
When the number of revolutions of 00 increases, the discharge amount of the hydraulic oil from the discharge port 102 increases, so that the hydraulic pressure generated by the oil pump device increases. And the rotor 200
When the number of rotations increases and the hydraulic pressure equal to or higher than the reference pressure (P1) is generated, the hydraulic pressure of the hydraulic oil from the discharge port 102 overcomes the urging force of the spring of the relief valve 300, so that the relief valve 300 is opened. In this way, excess hydraulic oil is discharged to the outside from the relief port of the relief valve 300.

[0005]

By the way, according to the oil pump device according to Japanese Utility Model Laid-Open No. 61-23485, two gear pumps are required, which is disadvantageous in terms of downsizing and is not suitable for a vehicle body or the like. When mounted on a substrate, it is disadvantageous in terms of mountability. Further, according to the oil pump device shown in FIG. 9, when the hydraulic pressure equal to or higher than the reference pressure (P1) is generated as described above, the relief valve 300 is opened by the hydraulic pressure of the hydraulic oil discharged from the discharge port 102. The excess hydraulic oil is discharged from the relief port to the outside. Therefore, since the large hydraulic pressure equal to or higher than the reference pressure (P1) is applied to the excess hydraulic oil discharged to the outside, the oil pump device is performing extra work, and the work in the oil pump device is performed. It is not preferable in terms of efficiency.

The present invention has been made in view of the above-mentioned circumstances, and its problem is that a plurality of suction oils are included in the surplus hydraulic oil discharged when the rotational speed of the rotor is increased and the required hydraulic pressure is secured. By adopting a means for feeding back pressure to a part of the port, it is possible to improve work efficiency, which is advantageous in reducing the driving horsepower of the oil pump, and is also advantageous in terms of downsizing. An object of the present invention is to provide an oil pump device capable of improving mountability when mounted on a base body.

[0007]

In the oil pump device according to the first aspect of the present invention, (a) a plurality of space groups whose volumes are changed by a rotor that is rotated by a drive source are formed, and the space groups are reduced. The side space communicates with the discharge port,
The enlarged side space is divided into a plurality of suction ports and communicates with each other, and an oil pump that feeds the working oil discharged from the discharge port to a fed portion, and (b) an operating state of the oil pump is described as follows. In a first state in which the suction ports are communicated with each other so that suction is performed in the enlarged side space, and the discharge port is communicated with at least one of the plurality of suction ports, and a part corresponding to the communicated suction ports The control valve that can be switched to the second state in which the hydraulic oil from the discharge port is pressure-fed is provided in the enlarged side space.

The gist of the invention of claim 2 is that the control valve comprises:
The switching control is performed on the basis of the hydraulic pressure in the supply passage. When the hydraulic pressure is smaller than a predetermined range, the switching is switched to the first state, and when the hydraulic pressure is higher than the predetermined range, the switching is switched to the second state. The gist of the invention according to claim 3 has a control means for detecting at least one of the hydraulic pressure, the oil temperature, the throttle opening degree, and the engine speed of the supply passage, and outputting the acquired control signal. The valve performs the switching control based on the control signal from the control means.

The gist of the invention of claim 4 is that the control valve comprises:
Based on the hydraulic pressure of the supply passage or the control signal of the control means, the operating state of the oil pump is changed to a first state in which the plurality of suction ports are communicated with each other to cause suction to the enlarged side space group, and the discharge state. The port is communicated with one of the plurality of suction ports, and the hydraulic oil from the discharge port is pressure-fed to a part of the enlarged side space corresponding to the communicated suction port to perform the suction operation only to the remaining enlarged side space. The purpose is to switch between the second state in which the operation is performed and the third state in which the discharge port is communicated with all the suction ports and the hydraulic oil from the discharge port is pressure-fed to the enlarged side space.

The fed portion of the present invention means an engine to which hydraulic oil is fed from a feeding oil passage, and a device such as a lubricating device such as a bearing, a cylinder or a piston of an internal combustion engine, which is oil-cooled. Alternatively, a hydraulically operated actuator or the like may be used.

[0011]

In the oil pump device according to the present invention, the rotation speed of the rotor increases as the rotation speed of the drive source increases, and the discharge amount of the hydraulic oil from the discharge port increases. Will increase. When the rotation speed of the drive source and the rotation speed of the rotor are small and the oil pressure in the supply path is smaller than the predetermined range (Pm), the control valve is in the first state, and the plurality of suction ports become one suction port and the expansion side. Hydraulic fluid is sucked into the space. Therefore, the oil pump sucks in the entire space on the enlarged side, and therefore, even if the rotation speed of the rotor is small, the necessary hydraulic pressure to be supplied to the supplied portion is secured.

On the other hand, when the rotation speed of the rotor increases and the discharge amount from the discharge port increases and the hydraulic pressure in the supply passage becomes larger than the predetermined range, the control valve sets the oil pump to the second state and the expansion side space is closed. Make only part of the air suck. This reduces the work of the pump and nevertheless ensures the required hydraulic pressure to be delivered to the delivered part. In other words, when the rotation speed of the drive source and the rotor increases, the discharge amount from the discharge port increases, the hydraulic pressure in the supply passage becomes larger than the predetermined range, and the required hydraulic pressure is secured only in the supply passage, the expansion is performed. Suction is not performed by causing suction in only a part of the side space and pumping excess hydraulic oil into the remaining enlarged side space.

In particular, as in the invention of claim 4, the first
~ If it is possible to switch to the third state, the low rotation speed range of the rotor,
Fine control is possible to supply the optimum amount of oil in the medium speed range and high speed range. In this way, the present invention returns the excess hydraulic oil to the expansion side space of the suction port,
The working oil circulates through the oil pump without suction in the enlarged side space, the extra work in the oil pump device is reduced or avoided, and the driving horsepower of the oil pump device can be reduced.

Further, when the required hydraulic pressure is secured only in the supply passage, extra work can be omitted and work efficiency is improved.
Unlike the device according to Japanese Utility Model Laid-Open No. 61-23485,
It is not necessary to equip two units integrally, which is advantageous for downsizing of the oil pump device and eventually for weight reduction. Therefore, it is advantageous for improving the mountability when mounted on a base body such as a vehicle body.

[0015]

BEST MODE FOR CARRYING OUT THE INVENTION An example of a first embodiment of an oil pump device according to the present invention will be described below. This example is mounted on a vehicle and rotated by a crankshaft of an internal combustion engine to generate hydraulic pressure. FIG. 1 shows a conceptual configuration diagram of the oil pump device. An oil pump 1 according to the oil pump device shown in FIG. 1 includes a pump body 1a made of metal (for example, an aluminum alloy or an iron alloy). A recess 1a1 is formed in the pump body 1a, and an outer rotor 3 that constitutes a driven gear having a large number of internal teeth 11 is rotatably fitted in the recess 1a1. Inside the outer rotor 3, an inner rotor 2 having an axis eccentric to the axis of the outer rotor 3 by a predetermined amount is rotatably arranged around the eccentric axis. The inner rotor 2 is connected to a crankshaft of an internal combustion engine as a drive source and rotates together with the crankshaft. The rotation speed of the inner rotor 2 is generally designed to be about 600 to 7,000 rpm.

The inner rotor 2 has a large number of outer teeth 21.
And an external gear portion that constitutes a drive gear including is formed. The inner teeth 11 and the outer teeth 21 are defined by a trochoid curve or a cycloid curve. The rotation direction of the inner rotor 2 is a counterclockwise direction (arrow A1 direction), and as the inner rotor 2 rotates, the outer teeth 21 of the inner rotor 2 enter the inner teeth 11 one after another, and the outer rotor 3 also moves in the same direction. Rotate. The outer teeth 21 and the inner teeth 11 form the pump chamber 10 divided into the spaces 22a to 22k shown in FIG. The space 22a shown in FIG. 1 has the largest volume, and the space 22f has the smallest volume.

Spaces 22b to 22 downstream of the space 22a
Since the volume of f (reduction side space) is gradually reduced, the discharge pressure is generated, and the action of discharging the hydraulic oil is obtained. Space 22
Spaces 22g to 22k (expansion side space) upstream of f are
Since the volume gradually increases, suction pressure is generated, and the suction action of the hydraulic oil is obtained. Pump body 1a of the oil pump 1
The discharge port 3 communicating with the spaces 22b to 22f.
3 are formed. The discharge port 33 is a port that discharges oil from the pump chamber 10 as the inner rotor 2 rotates. A suction port 31 is formed separately in the pump body 1a into a suction port A and a suction port B. The suction port A communicates with the spaces 22g to 22i, and the suction port B communicates with the space 22k.

In this embodiment, the suction port B is located downstream of the suction port A in the rotational direction indicated by the arrow A1. The opening area of the suction port A is set to be larger than the opening area of the suction port B. FIG.
As can be understood from the above, the contact point E between the inner teeth 11 and the outer teeth 21
The suction port A and the suction port B are divided by 1 and E2. Therefore, the suction port A and the suction port B do not communicate with each other in the circumferential direction of the pump chamber 10, and therefore the suction port A and the suction port B have a suction function independent of each other. Further, the suction port A is communicated with a suction pipe line 66 extending to an oil storage section 69 such as an oil pan, a reservoir, an oil tank. Of course, a part of the hydraulic oil fed to the fed portion 80 is returned to the oil storage portion 69.

The supply passage 5 communicating with the discharge port 33 is a passage for leading out the hydraulic oil to the feeding portion 80 of the internal combustion engine, and has a branch passage 6A and a branch passage 6B in the middle thereof. The tip of the branch path 6A is connected to the control port 71 of the spool-type control valve 7,
The tip of the branch path 6B is connected to the third intermediate port 72 of the control valve 7.
It is connected to the. The control valve 7 has a valve body 77 axially slidably disposed in a valve chamber 78 formed in the pump body 1 a of the oil pump 1, and the valve chamber 78 is always provided in the control port 71. The first valve portion 77a that forms the head chamber 75 that communicates with the inside of the valve chamber 78 and the valve body 77 are always provided in the head chamber 7
And a second valve portion 77b that forms a back chamber 79a that accommodates a telescopic spring 79 that biases the valve chamber 5 in the valve chamber 78. The first valve portion 77a and the second valve portion 77b are connected by a small-diameter shaft portion, whereby both valve portions 77a,
A valve passage 76 is formed between 77b. The valve chamber 78 has a first intermediate port 73 communicating with the suction port A via the passage 62 and a second intermediate port 73 communicating with the suction port B via the passage 63.
An intermediate port 74 and a third intermediate port 72 communicating with the branch path 6B are formed. In the first intermediate port 73, the valve body 77 is provided with the expansion spring 7 by the hydraulic pressure in the head chamber 75.
By sliding against 9 the valve chamber 78 is controlled so that the communication between the control port 71 and the second intermediate port 74 via the head chamber 75 and the valve passage 76 is controlled by the first valve portion 77a. Has an opening inside, and the third intermediate port 72
Is opened in the valve chamber 78 so that the sliding of the valve body 77 controls the opening and closing of the communication with the second intermediate port 74 via the valve passage 76 by the second valve portion 77b. The second
The intermediate port 74 is always open to the valve passage 76.

Therefore, depending on the position of the valve body 77, the control valve 7
Indicates the operating state of the oil pump 1 in the first state (the first and second intermediate ports 73 and 74 are in communication with each other through the valve passage 76 and the suction ports A and B are in communication with each other);
The state (a state in which the third intermediate port 72 and the second intermediate port 74 communicate with each other through the valve passage 76 and the branch passage 6B communicates with the suction port B) and the third state (the control port 71 and the first intermediate port 73). Branch path 6A communicating with the head chamber 75
Is connected to the suction port A). The first state corresponds to FIG. 1, the second state corresponds to FIG. 2, and the third state corresponds to FIG. still,
The passages 62 and 63, the branch passages 6 </ b> A and 6 </ b> B, a portion of the suction pipe passage 66, and a portion of the supply passage 5 are similar to the control valve 7 in the oil pump 1.
Is formed on the pump body portion 1a. Further, the back chamber 79a is provided with a pressure relief hole 79b.

Now, the operation of the oil pump device of this example will be described. In a low rotation range where the rotation speed of the crankshaft rises from zero, the force of the expansion spring 79 exceeds the hydraulic pressure of the supply passage 5, and the control valve 7 causes the intermediate passages 73 and 74 to move in the valve passage 76 as shown in FIG. Communication Suction port A and suction port B are communicated with each other. The fact that both suction ports A and B communicate with each other means that the spaces 22g to 22k are suctioned,
The oil pump 1 sucks the hydraulic oil in the oil storage unit 69 into the suction conduit 6
Suction through space 22g-22k through 6, space 22b
Discharge to the discharge port 33 from ~ 22e. The discharged hydraulic oil is supplied from the supply passage 5 to the internal combustion engine.

At this time, the low rotation speed range (rotation speed 0 <
N ≦ N1). In FIG. 5, the characteristic α
Is a discharge characteristic when suction is performed in both suction ports A and B, and characteristic β is a discharge characteristic when suction is performed in either suction port A or B. The characteristics in the low rotation range match the characteristics α. As described above, when the rotation speed of the internal combustion engine is in the low rotation range, normal suction and discharge are performed, and the required oil pressure is sufficiently secured (first state).

On the other hand, when the rotation speed of the internal combustion engine increases and exceeds the boundary value N1 between the low rotation speed region and the middle rotation speed region (the rotation speed of the internal combustion engine is, for example, 1500 rpm), the inner rotor 2
The number of rotations of increases. In this case, since the discharge amount of the hydraulic oil from the discharge port 33 increases, the hydraulic pressure of the hydraulic oil in the supply passage 5 also rises according to the boundary value N1 and becomes larger than the predetermined range (Pm). Due to this hydraulic pressure, the valve body 77 slides to the right in the figure against the expansion spring 79 in FIG. 1, and as shown in FIG. 4, in the first half of the middle rotation range, the control valve 7 has the valve body 7
The first valve portion 77a of No. 7 opens a part of the first intermediate port 73 into the valve passage 76, and the second valve portion 77b of the second intermediate portion 7b.
It is located in a transient state in which a part of the fourth and third intermediate ports 72 is opened to the valve passage 76. In this transitional state, suction is performed at the suction port A (spaces 22g to 22i), and a part of the passage 62 is opened at the suction port B (space 22k) so that the first intermediate port 73 and the valve passage are throttled. Suction is made via 76, the second intermediate port 74 and the passage 63 (the suction is restricted at the suction port B). At the same time, the suction port B communicates with the branch passage 6B through the passage 63, the second intermediate port 74, the valve passage 76, and the third intermediate port 72 which is throttled by opening a part thereof. Part of the hydraulic oil to be fed to the fed portion 80 of the internal combustion engine is sucked (pressure-fed) at the suction port B. At this time, the characteristic of the first half (N1 <N <N2) of the middle rotation range shown in FIG. 5 is obtained. When the rotation speed of the internal combustion engine further increases to N2 or more, the rotation speed of the inner rotor 2 also increases, the discharge amount of the hydraulic oil from the discharge port 33 increases, and the hydraulic pressure of the hydraulic oil in the supply passage 5 further increases. .
As can be understood from FIG. 2, this hydraulic pressure moves the valve body 77 to the right side in the drawing, connects the second intermediate port 74 to the valve passage 76, and closes the first intermediate port 73. When the first intermediate port 73 is closed, the pump operation for sucking the hydraulic oil in the oil storage unit 69 is performed in the spaces 22g to 22i (second state).

In the latter half of the middle speed range, the third intermediate port 72 communicates with the branch passage 6B, and a part of the hydraulic oil to be fed to the internal combustion engine branches off from the branch passage 6B → valve passage 76 →
It is pumped to the suction port B via the passage 63. Therefore, the space 22k communicating with the suction port B does not suck, the working oil is pressure-fed to the space 22k by the discharge pressure, and the work of the oil pump 1 is performed only by 22g to 22i communicating with the suction port A. The ejection characteristics at this time are as shown in FIG.
Since the characteristic of the suction port B is reduced from the increase characteristic in the low speed range, the suction work of the oil pump 1 is reduced and the hydraulic pressure required for the internal combustion engine can be efficiently obtained (medium speed range). In the present embodiment, in FIG. 5, the transient state described above is switched to the second state at the rotation speed N2 where the characteristic line in the first half of the middle rotation range intersects the characteristic β. The number can be increased or decreased by appropriately changing the position of the first intermediate port 73, and can be changed according to the specifications of the internal combustion engine. Note that in these cases, after switching to the second state, the ejection characteristics immediately follow the characteristic β.

When the rotation speed of the internal combustion engine further increases and exceeds the boundary value N3 between the middle rotation speed region and the high rotation speed region, the hydraulic pressure of the hydraulic oil in the supply passage 5 also increases, and the valve element 77 of the control valve 7 moves further to the right. And the branch passage 6A is also communicated with the suction port A. As a result, the space 22g-2
The hydraulic oil is pumped to 2i and 22k (third state). That is, a part of the hydraulic oil sent to the supply path 5 circulates in the oil pump 1 to reduce pump work.

The discharge characteristic at this time exhibits an increase characteristic similar to that in the middle rotation speed region as the rotation number thereafter increases, as shown in the region of the rotation number N3 or higher in FIG. In this way, in the present embodiment, since the hydraulic oil in the supply passage is pressure-fed in stages to the plurality of suction ports in accordance with the rotation speed (hydraulic pressure), only the necessary amount of hydraulic oil is supplied on the internal combustion engine side according to the rotation speed. It is possible to reduce the driving horsepower of the oil pump while feeding. Especially,
Since only the required amount of oil on the internal combustion engine side is sucked at high speed, it is not necessary to enlarge the suction passage, for example, the strainer. Further, since it is possible to set with one set of rotors for an oil pump integrally provided with two gear pumps as in Japanese Utility Model Laid-Open No. 61-23485, it is advantageous for downsizing and weight saving of the oil pump. The mountability of the oil pump on the vehicle body is improved.

The present invention will be further described with reference to the second embodiment shown in FIGS. 6 and 7. In the embodiment of FIG.
The configuration for communicating the suction ports A and B in the low rotation speed region is the same as that of the first embodiment, but the working oil from the branch passage 6A that drives the control valve 9 in the middle rotation speed region and the high rotation speed region is directly sucked into the suction port B. In this configuration, the branch path 6B of the first embodiment is omitted so that the branch path 6B is omitted.

That is, the control valve 9 is branched from the supply passage 5 and the head chamber 95 is communicated with the branch passage 6A formed in the pump body 1a, and the expansion spring 99 is accommodated in the valve body 97 with hydraulic oil having a discharge pressure. The configuration is such that it is simply pushed to the side of the fitted back chamber 99a. Then, in the valve chamber 98, the passage 62
A first intermediate port 93 which is an opening to the passage 63, a second intermediate port 94 which is an opening to the passage 63, and a control port 91 which is an opening to the branch passage 6A are formed, and the second intermediate port 94 is substantially formed. A side passage 94a is formed so that it is made longer than the length of the second valve portion 97b in the stroke direction. In addition,
A pressure release hole 99b is formed in the back chamber 99a. Further, the first valve portion 97a always partitions the back chamber 99a and the first intermediate port 93.

Even with the above-described structure, the ejection characteristic as shown in FIG. 5 is exhibited as in the first embodiment. First, in the valve body 97, the force of the expansion spring 99 is superior to the hydraulic pressure in the low rotation range,
As shown in, the first intermediate port 93 and the second intermediate port 94
Is in a position where they are communicated with each other via the valve passage 96 (first state), and the oil pump 1 is operated so that the suction ports A and B communicate with each other to perform a suction operation, thereby performing the maximum pump work represented by the characteristic α. To do. At the hydraulic pressure in the first half of the middle speed range, the valve body 97
As shown in FIG. 7A, the first intermediate port 93 and the second intermediate port 94 are communicated with each other through the valve passage 96, and the head chamber 95 and the passage 63 are communicated with each other through the side passage 94a. It is the position of the transient state. In this case, the suction port A has the expanding space 22g to 2 as in the first embodiment.
At the same time, the hydraulic oil in the oil storage section 69 is sucked into the suction port B from the throttled second intermediate port 94, and at the same time, one of the hydraulic oil discharged from the supply passage 5 is passed through the side passage 94a. The parts are pressure-fed from the branch path 6A. Even in this transient state, the path for sucking a part of the discharged hydraulic oil is changed to a path for directly pumping the hydraulic oil directly from the branch path 6A for moving the valve element 97 to the suction port B. First half of 5 mid-speed range (N1 <N <N2)
The same as the characteristic of the above, and the work of the pump is reduced by the amount that the hydraulic oil having the discharge pressure from the branch passage 6A is pumped to the suction port B. Next, for the hydraulic pressure in the latter half of the medium speed range, as shown in FIG.
As shown in (B), the valve body 97 moves to a position where the first intermediate port 93 and the second intermediate port 94 are separated by the second valve portion 97b, and the hydraulic oil having the discharge pressure from the branch passage 6A is moved to the side. Pressure is fed to the suction port B through the passage 94a (second state). Also in this case, the characteristics of the latter half of the middle rotation range (N2 <N <N3) in FIG. 5 are the same except that the route for sending the hydraulic oil of the discharge pressure is the same, and the operation of the discharge pressure from the branch passage 6A to the suction port B The pump work is reduced as the oil is pumped. When the number of revolutions further increases and the hydraulic pressure in the high revolution range is reached, Fig. 7 (C)
As shown in FIG. 6, the valve body 97 moves to a position where the second valve portion 97b is on the left side of the first intermediate port 93 in the drawing, and the branch passage 6
The third state is established in which A and the passages 62 and 63 are communicated with each other, and hydraulic oil having a discharge pressure is pumped to the suction ports A and B. As a result, hydraulic oil having a discharge pressure is pumped to both the suction ports A and B, and the characteristics are the same as N3 or higher in FIG. 5, and pump work is reduced.

As described above, according to the second embodiment as well, the pump work can be reduced in the medium rotation range and the high rotation range, but in the second embodiment, it is necessary to provide the branch passage 6B of the first embodiment. Since the pump body 1a is compact, the mountability on the internal combustion engine is improved.
By the way, in each of the above-described embodiments, the suction port 31 is separated into two A and B in the above embodiment 1, but the number of separations may be further increased. In this case, the passages 62 and 63 may be increased corresponding to the increase of the suction ports, and the number of ports of the control valves 7 and 97 and the number of valve portions may be changed.

FIG. 8 further shows a third embodiment. In this example, the control valve 7 is driven by a well-known proportional electromagnetic control means 90. An electric control device 9 for generating an output signal according to the oil pressure of the supply passage 5, the oil temperature, the throttle opening, and the rotation speed of the internal combustion engine.
The proportional electromagnetic control means 90 is controlled by the output signal of 1. Since the basic configuration other than the proportional electromagnetic control means 90, the electric control device 91, and the control valve 7 is the same as the example shown in FIG. 1 described above, parts having the same functions are designated by the same reference numerals and will be described. Is omitted.

In this example, the oil pressure of the supply passage, the oil temperature, the throttle opening, and the rotational speed of the internal combustion engine are detected directly or indirectly, and based on the detection signal, the characteristics of FIG.
It is possible to change the characteristics in the middle rotation range by controlling 1 and N2. In addition, the present invention can be applied to an oil pump device used for other industrial equipment other than a vehicle, and is not limited to a trochoidal type oil pump, and the driving form of the pump is not limited to the crankshaft direct drive type, for example, a timing belt. It is also possible to appropriately select such as a pulley drive type or the like.

[Brief description of drawings]

FIG. 1 is a configuration diagram of an oil pump device in a state where a rotor is in a low rotation range according to a first embodiment of the present invention.

FIG. 2 is an operation explanatory diagram of the oil pump device in a state where the rotor is in a middle rotation range (second half).

FIG. 3 is an operation explanatory view of the oil pump device when the rotor is in a high rotation range.

FIG. 4 is an operation explanatory view of the control valve in a state of a middle rotation range (first half).

FIG. 5 is a discharge characteristic diagram of the oil pump device.

FIG. 6 is a configuration diagram of an oil pump device according to a second embodiment of the present invention in a low rotation speed region.

FIG. 7: The first half (A) of the middle rotation range of the oil pump device,
It is operation | movement explanatory drawing in the middle rotation range latter half (B) and a high rotation range (C).

FIG. 8 is a configuration diagram of an oil pump device according to a third embodiment of the present invention.

FIG. 9 is a configuration diagram schematically showing a conventional oil pump device.

[Explanation of symbols]

In the figure, 1 is an oil pump, 1a is a pump body, 10 is a pump chamber, 11 is internal teeth, 2 is a rotor, 21 is external teeth, 31
Is a suction port A, B, 33 is a discharge port, 5 is a supply passage,
6A and 6B are branch pipes, and 7 and 9 are control valves, and the same or equivalent elements in each figure are denoted by common reference numerals.

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Sadanori Miura 2-1-1 Asahi-cho, Kariya city, Aichi Aisin Seiki Co., Ltd.

Claims (4)

[Claims] 1. A plurality of space groups whose volumes are changed by a rotor that is rotated by a drive source, and a reduction side space of the space groups communicates with a discharge port, and an expansion side space has a plurality of suction ports. And an oil pump for communicating hydraulic oil discharged from the discharge port to the supply target portion, and an operating state of the oil pump by connecting the plurality of suction ports to each other on the enlarged side. First to let the space suck
And a second state in which the discharge port is communicated with at least one of the plurality of suction ports and the hydraulic oil from the discharge port is pressure-fed to a part of the enlarged side space corresponding to the communicated suction port. An oil pump device, comprising: 2. The control valve performs the switching control based on the hydraulic pressure of the discharge port, switches to the first state when the hydraulic pressure is lower than a predetermined range, and the hydraulic pressure is lower than the predetermined range. The oil pump device according to claim 1, wherein the oil pump device is switched to the second state when it is large. 3. A control means for detecting at least one of the operating oil pressure of the discharge port, the oil temperature, the throttle opening, and the engine speed, and outputting a control signal obtained by the control means. The oil pump device according to claim 1, wherein the switching control is performed based on a control signal from the control means. 4. The control valve controls the operating state of the oil pump based on the hydraulic pressure of the discharge port or the control signal of the control means to the enlarged side space group by communicating the plurality of suction ports with each other. A first state that causes suction,
The discharge port is communicated with one of the plurality of suction ports, and hydraulic oil from the discharge port is pressure-fed to a part of the enlarged side space corresponding to the communicated suction port to perform suction operation on the remaining enlarged side space. And a third state in which the discharge port communicates with all the suction ports and the hydraulic oil from the discharge port is pumped to the enlarged side space. The oil pump device according to claim 1.