JP2018145867A - Oil pump - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent the occurrence of vibration and noise by preventing abnormal high pressure without lowering the mechanical efficiency of an oil pump.SOLUTION: A notch groove 9 communicated with an oil discharge port 4 is formed in one inner peripheral face in the axial direction which forms an internal space 5 of a casing 2 and with which the bottom face of an outer rotor 6 has slide contact. The notch groove 9 is constructed at a two-stage depth with a first notch groove 9a communicated with one lock-in part 8 in the stage that the lock-in part performs predetermined-pitch rotation after finishing a suction stroke, and a second notch groove 9b continuous with the first notch groove 9a, deeper than the first notch groove 9a, and shallower than the oil discharge port 4. The depth of the first notch groove 9a is 0.8-2.0% of the thickness of the outer rotor 6, and the depth of the second notch groove 9b is 4.0-35% of the thickness of the outer rotor 6.SELECTED DRAWING: Figure 1A

Description

  The present invention relates to an oil pump for an automobile engine, and more particularly, to an oil pump that performs a pump action by changing the volume of a confined portion between an inner rotor and an outer rotor.

  Conventionally, as shown in FIGS. 6A to 6E, an oil pump 101 including a rotor chamber 105 having an oil suction port 103 and an oil discharge port 104, an outer rotor 106, and an inner rotor 107 is known. In particular, the oil pump 101 for automobiles is used in a state in which many air bubbles B are contained in the oil (working oil, lubricating oil). This is because bubbles B are mixed in the oil and stirred by the operation of the automobile and the movement of the operating equipment.

  If a large number of bubbles B are present in the oil, a negative pressure is generated when the oil is sucked. Therefore, as shown in FIG. 6A, the bubbles B expand to suppress the suction filling and the filling rate is insufficient. The inhalation stroke ends.

  The closing portion 108 formed by the suction path, the closing path, the inner rotor 107 having the outer teeth 107a, and the outer rotor 106 having the inner teeth 106a becomes negative pressure when the suction is completed, and the inner rotor As shown by the broken lines in FIGS. 6B to 6D and FIG. 3, the pressure in the confining portion 108 varies greatly due to the rotation of 107 and the rotation of the outer rotor 106 that follows the rotation. Then, as shown in FIG. 6E, when it is connected to the oil discharge port 104, high-pressure oil flows in abruptly, causing the same phenomenon as the water hammer effect, generating abnormally high pressure and worsening vibration and noise.

  Therefore, for example, the oil pump disclosed in Patent Document 1 includes a shallow groove formed on the locus of the root position by rotation of the outer rotor on the start end side of the discharge port, and the end portion of the suction port and the discharge port The sealed space is communicated with the shallow groove in a state where the sealed space formed by the partition portion, the outer rotor, and the inner rotor between the first end portion and the inner rotor is reduced from the maximum.

  Moreover, in the trochoid oil pump of patent document 2, the housing groove | channel which consists of shallow grooves is expanded to the outer periphery of an outer rotor, and a rotor groove | channel (radiation groove | channel) is formed toward the radial direction side rather than a tooth | gear bottom part. .

JP-A-2005-42689 JP 61-138893 A (particularly FIG. 7)

  When the radiating groove is provided in the outer rotor as in Patent Document 2, the oil leaks from the radiating groove due to a clearance for rotation of the outer rotor and the amount of supplied oil may be reduced and the mechanical efficiency may be reduced. . On the other hand, in the thing of patent document 1, the pressure control in a shallow groove is not fully performed.

  The present invention has been made in view of this point, and an object of the present invention is to prevent generation of vibration and noise by preventing abnormal high pressure without reducing mechanical efficiency.

  In order to achieve the above object, in the present invention, the pressure of the confining portion is gradually increased through the notch groove to prevent the occurrence of abnormal high pressure.

Specifically, in the first invention, an oil suction port, an oil discharge port, a casing having an internal space communicating with the oil suction port and the oil discharge port,
An outer rotor having a predetermined number of teeth, which is rotatably accommodated in the internal space;
The external teeth that mesh with the inner teeth of the outer rotor from the inside are one less than the number of teeth of the inner teeth, and are accommodated inside the outer rotor so as to be rotatable around an axis that is eccentric to the outer rotor, An oil pump comprising an inner rotor that forms a plurality of confinement portions with the outer rotor,
A predetermined gap is provided between the end portion of the oil suction port and the start end portion of the oil discharge port,
A notch groove that communicates with the oil discharge port is formed on one inner peripheral surface in the axial direction in which the outer rotor slides, which forms the internal space of the casing,
The notch groove includes a first notch groove that communicates with the closed portion when the single closed portion rotates a predetermined pitch from the stage where the suction stroke is completed, and the first notch groove that is continuous with the first notch groove. A depth of at least two stages including a second notch groove deeper than the notch groove and shallower than the depth of the oil discharge port;
The first notch groove has a depth of 0.8% to 2.0% with respect to the thickness of the outer rotor,
The second notch groove has a depth of 4.0% to 35% with respect to the thickness of the outer rotor.

  According to the above configuration, the depth of the notch groove communicating with the oil discharge port is set to two stages, so that high-pressure oil from the oil discharge port is prevented from suddenly flowing into the confined portion, and is the same as the hydraulic action Occurrence of the phenomenon is prevented. Also, if the first notch groove is shallower than 0.8% with respect to the thickness of the outer rotor, the high pressure oil from the oil discharge port does not properly flow into the confining part due to excessive restriction, and is less than 2.0% If it is deepened, the high-pressure oil will suddenly flow into the confining part and the pressure fluctuation cannot be suppressed. If the second notch groove is shallower than 4.0% with respect to the thickness of the outer rotor, the high pressure oil does not flow properly into the first notch groove. The pressure fluctuation cannot be suppressed by flowing too much into the groove. However, when the depth of the first notch groove and the second notch groove is within an appropriate range as in the above configuration, pressure fluctuation in the confinement portion can be effectively suppressed. The predetermined interval between the terminal end portion of the oil suction port and the start end portion of the oil discharge port is, for example, an interval that is 1.1 times or more and 1.2 times or less of an internal tooth pitch that is an internal tooth interval.

In the second invention, in the first invention,
The notch groove is formed on an inner peripheral surface opposite to the inner peripheral surface on which the oil discharge port is formed, of the inner peripheral surface in the axial direction in which the outer rotor slides, which forms the inner space of the casing. And is configured to communicate with the oil discharge port via the closing portion.

  According to said structure, by providing a notch groove in the internal peripheral surface on the opposite side to an oil discharge port, oil communicates with a 2nd notch groove and an oil discharge port via a confinement part.

In the third invention, in the first or second invention,
Immediately before the closed portion communicates with the oil discharge port, the area of the region where the first notch groove communicates with the closed portion in plan view is 0.2 times the area of the closed portion. More than 0.4 times.

  According to the above configuration, since the area of the oil flowing into the notch groove in the plan view is an appropriate size that is not too small and not too small, the oil appropriately flows from the first notch groove to the closing portion, Sudden pressure fluctuations at the part are prevented.

In a fourth invention, in any one of the first to third inventions,
As one of the confining portions rotates toward the oil discharge port, the area of the region where the first notch groove and the confining portion communicate with each other in plan view gradually increases with respect to the area of the confining portion. It is comprised so that it may become large.

  According to said structure, oil distribute | circulates by moderate speed between a notch groove and an oil discharge port by gradually increasing the area of the area | region to communicate.

In a fifth invention, in any one of the first to fourth inventions,
The first notch groove is formed so as to communicate with the confinement portion at a position advanced from 0.02 to 0.06 times the internal tooth pitch from the stage where one confinement portion has completed the suction stroke. Has been.

  According to said structure, by setting appropriately the timing which connects a 1st notch groove and a confinement part, the pressure of a confinement part is raised gradually and generation | occurrence | production of the same phenomenon as a hydrodynamic action is prevented. Can do.

  As described above, according to the present invention, the notch groove that communicates with the oil discharge port is formed on one inner peripheral surface in the axial direction in which the outer rotor slides, which forms the internal space of the casing, and the notch groove is formed. A first notch groove that communicates with the confined portion when the single confined portion rotates a predetermined pitch from the stage where the intake stroke is completed, and a depth that is continuously deeper than this and shallower than the depth of the oil discharge port. The first notch groove has a depth of 0.8% or more and 2.0% or less with respect to the thickness of the outer rotor, and the second notch groove has a thickness of the outer rotor. With the depth of 4.0% or more and 35% or less, oil leakage does not occur from the radiating groove as in the conventional case, and abnormal high pressure in the confinement part is reduced without reducing mechanical efficiency. Prevent generation of vibration and noise It can be prevented.

In the oil pump which concerns on embodiment of this invention, it is an axial sectional view which shows the outer rotor of the state which the suction stroke was complete | finished, an inner rotor, and its periphery, and the notch groove. It is a top view equivalent to FIG. 1A which shows the notch groove communication immediately before. FIG. 1B is a plan view corresponding to FIG. 1A showing a state advanced by 0.084 pitch. FIG. 1B is a plan view corresponding to FIG. 1A and an axial sectional view showing a state immediately before the discharge stroke. It is a top view equivalent to FIG. 1A which shows the state connected to the oil discharge port. It is a top view which shows the oil pump which removed the cover and made the inside visible. It is a top view which takes out and shows an inner rotor and an outer rotor. It is a graph which shows the pressure fluctuation in the confinement part of the oil pump which concerns on embodiment of this invention with a notch groove, and the oil pump of the past (comparative example) without a notch groove. It is a graph which shows the relationship between the frequency and vibration acceleration of a comparative example with and without a notch groove. It is a graph which shows the influence of the groove depth of a 20th-order vibration acceleration of the comparative example with and without a notch groove. In the oil pump which concerns on the comparative example of embodiment of this invention, it is the top view which made visible the outer rotor, inner rotor, and its periphery of the state which the suction stroke was complete | finished. FIG. 6B is a plan view corresponding to FIG. 6A, showing just before the notch groove communication. FIG. 6B is a plan view corresponding to FIG. 6A showing a state advanced by 0.084 pitch. FIG. 6B is a plan view corresponding to FIG. 6A showing immediately before the discharge stroke. FIG. 6B is a plan view corresponding to FIG. 6A showing the end of notch groove communication.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings.

  FIG. 2A shows an oil pump 1 according to an embodiment of the present invention, and the oil pump 1 includes a casing 2 made of cast metal, for example. In FIG. 2A, the disc-shaped cover 2a is omitted. The casing 2 includes an oil suction port 3, an oil discharge port 4, and an internal space 5 having a circular cross section that communicates with the oil suction port 3 and the oil discharge port 4. In this internal space 5, an outer rotor 6 having a predetermined number of teeth (11 in this embodiment) of internal teeth 6a is rotatably accommodated.

  As shown in FIG. 2B, an inner rotor 7 is disposed inside the outer rotor 6. The inner rotor 7 has one outer tooth 7a meshing with the inner tooth 6a from the inside by one less than the number of teeth (N + 1) of the inner tooth 6a (the number of teeth N). The center Oout is accommodated so as to be rotatable about the center Oin of the eccentric shaft, and serves to form a plurality of confining portions 8 between the outer rotor 6 and the center Oout. The inner rotor 7 is connected to a crankshaft of an engine (not shown), for example. That is, the inner rotor 7 is driven by the engine around Oin, and the inner rotor 7 drives the outer rotor 6 dynamically around Oout.

  As shown in FIG. 1A, the gap between the end portion 3a of the oil suction port 3 and the start end portion 4a of the oil discharge port 4 is, for example, 1.1 times or more the internal tooth 6a pitch P which is the interval between the internal teeth 6a. An interval θ0 that is equal to or less than twice is provided (1.1 ≦ θ0 ≦ 1.2).

  As shown in part in a cross-sectional view in FIG. 1A, a notch is formed on the inner peripheral surface of the cover 2 a that forms an internal space 5 of the casing 2 and is in sliding contact with the surface opposite to the oil discharge port 4 of the outer rotor 6. A groove 9 is formed. The notch groove 9 is processed by an end mill or the like, and a first notch groove 9a that communicates with the confinement portion 8 when the single confinement portion 8 rotates a predetermined pitch from the stage where the suction stroke is completed, and the first notch groove. The second notch groove 9b is formed at least in two stages deeper than the first notch groove 9a and shallower than the depth of the oil discharge port 4 continuously from 9a. In FIGS. 1A to 1E, the cover 2a is omitted, and the notch groove 9 is indicated by a broken line.

  Here, the depth H1 of the first notch groove 9a is 0.8% or more and 2.0% (0.008H0 ≦ H1 ≦ 0.02H0) with respect to the thickness H0 of the outer rotor 6. The depth H2 of the second notch groove 9b is 4.0% to 35% (0.04H0 ≦ H1 ≦ 0.35H0) with respect to the thickness H0 of the outer rotor 6.

  For example, the thickness H0 of the outer rotor 6 is 12 mm, the depth H1 of the first notch groove 9a is 0.2 mm (1.7% of H0), and the depth H2 of the second notch groove 9b is 0.5 mm (H0). 4.2%), the depth of the inlet of the discharge port 4 is H3 = 0.8 mm (6.7% of H0).

  As will be described in detail later, in the present embodiment, the first notch groove 9a is a position θ1 advanced from 0.02 times to 0.06 times the internal tooth pitch from the stage where one confining portion 8 has finished the suction stroke. (0.02P ≦ θ1 ≦ 0.06P) so as to communicate with the confinement portion 8.

  As shown in an enlarged view in FIG. 1D, immediately before the closing portion 8 communicates with the oil discharge port 4, the area S1 of the region where the first notch groove 9a and the closing portion 8 communicate with each other in a plan view is closed. They are 0.2 times or more and 0.4 times or less with respect to the area S0 of the embedding part 8 (0.2S0 <= S1 <= 0.4S0). The downstream side of the second notch groove 9b intersects one end of the oil discharge port 4 in plan view.

  The area S1 of the region where the first notch groove 9a and the closing part 8 communicate with each other in plan view as one closing part 8 rotates toward the oil discharge port 4 is the area of the closing part 8. It is comprised so that it may become large gradually with respect to S0.

  Next, the operation of the oil pump 1 according to this embodiment will be described.

  As shown in FIG. 1A, in the state where the suction stroke is completed, the air bubbles B in the oil expand due to the negative suction pressure, and the confining portion 8 cannot be sufficiently filled with oil.

  Next, as shown in FIG. 1B, the first notch groove 9a and the confining portion 8 begin to communicate with each other at the position θ1 of about 0.04P (0.02P ≦ θ1 ≦ 0.06P), and the bubble B is obstructed. Without this, the pressure in the confinement portion 8 gradually increases.

  Next, as shown in FIG. 1C, for example, at a position of about 0.084P, the oil flows out from the closed portion 8 into the notch groove 9, and the gauge pressure temporarily decreases as shown by the solid line in FIG.

  Next, when the rotation further proceeds, the pressure increases due to the reduction of the volume of the confinement portion 8, but since the communication with the notch groove 9, the increase in pressure is suppressed as shown by the solid line in FIG. 3. It is done.

  Next, as shown in FIG. 1D, immediately before the cover discharge port (0.1 to 0.2 P) and thereafter, a rapid oil inflow from the oil discharge port 4 is suppressed, and hydraulic pulsation and mechanical vibration are reduced. The bubble B has almost disappeared.

  Next, as shown in FIG. 1E, the notch groove 9 and the confining portion 8 communicate with each other even when approaching the end position of the notch groove 9.

  This cycle is performed in the same manner at the next confinement portion 8.

  In the present embodiment, the depth of the notch groove 9 communicating with the oil discharge port 4 is set to two stages of the first notch groove 9a and the second notch groove 9b deeper than the first notch groove 9a. Since the area S1 in plan view of the portion where the oil flows between them is set to an appropriate size that is not too small and not too small, the oil appropriately flows into the confining portion 8 from the first notch groove 9a and the second notch groove 9b. A sudden pressure fluctuation at the confining portion 8 is prevented.

  Further, by gradually increasing the ratio of the depth of the first notch groove 9a, the second notch groove 9b and the oil discharge port 4 to the thickness of the outer rotor 6, the confining portion 8 and the oil discharge port 4 Oil circulates gently between the two.

  Furthermore, by appropriately setting the timing of communication with the first notch groove 9a, it is possible to prevent the same phenomenon as the hydrodynamic action from occurring and prevent the pressure of the confining portion 8 from rising rapidly.

  Next, as a comparative example, in the case where the notch groove 9 is not provided, the result of examining the change in gauge pressure in the same oil pump in other configurations is shown by a broken line in FIG. In this comparative example, bubbles expand due to the negative suction pressure at the end of the suction, and as shown by the broken line in FIG. 3, the rising of the pressure is delayed because the closed portion cannot be filled with oil. In FIGS. 6A and 6B, the bubble B is generated as in FIGS. 1A and 1B. However, in FIG. 6C around 0.084P, the bubble B is not reduced as in FIG. As can be seen in FIG. 3, the pressure continues to rise. In FIG. 6D which has advanced by 0.14P, the bubbles B remain, and the pressure increases rapidly as seen in FIG.

  In the comparative example, since the pressure of the confining portion 108 is low and the oil discharge port 104 is connected, the oil suddenly flows from the oil discharge port 104 due to a large pressure difference, causing hydraulic pulsation and mechanical vibration.

  However, in the present embodiment, as indicated by a solid line in FIG. 3, the gauge pressure in the confining portion 8 is suppressed as much as possible. As a result, as shown in FIG. 4, the acceleration and noise effects were improved by 3 dB as compared with the comparative example. When the communication position of the first notch groove 9a is made closer to 0.03 times the pitch P of the inner teeth 6a, the oil in the confining portion 8 tends to flow backward to the oil suction port 3 and is 0.05 times as much. If it is further away, the region of the notch groove 9 may become too narrow.

  On the other hand, in FIG. 5, the depth of the first notch groove 9a is 0.10 mm (0.8%), 0.15 mm (1.25%), 0.25 mm (2.1%), 0.35 mm (2. 9%) shows the change in vibration acceleration (dB). A comparative example without the notch groove 9 is also shown for reference. In particular, at 600 Hz to 800 Hz, which is frequently used, vibration acceleration in the case of 0.15 mm was the lowest. Although 0.10 mm and 0.25 mm were inferior to 0.15 mm, the vibration acceleration decreased. Although 0.35 mm was the least effective, it was found that the vibration acceleration was lower than that of the comparative example.

  Therefore, according to the oil pump 1 according to the present embodiment, oil leakage does not occur, and abnormal high pressure can be prevented and generation of vibration and noise can be prevented without reducing mechanical efficiency.

(Other embodiments)
The present invention may be configured as follows with respect to the above embodiment.

  That is, in the said embodiment, although the notch groove 9 was provided in the cover member 2a, you may provide in the casing 2 side. That is, a notch groove 9 that communicates with the oil discharge port 4 may be formed on the inner peripheral surface that forms the internal space 5 of the casing 2 and that is in sliding contact with the bottom surface of the outer rotor 6. In this case, it is easy to adjust the positional relationship with the starting end portion 4a of the oil discharge port 104 when the notch groove 9 is processed.

  In addition, the above embodiment is an essentially preferable illustration, Comprising: It does not intend restrict | limiting the range of this invention, its application thing, or a use.

1 Oil pump
2 Casing
3 Oil intake port
3a Termination
4 Oil discharge port
4a Start end
5 Internal space
6 Outer rotor
6a Internal teeth
7 Inner rotor
7a external teeth
8 Containment
9 Notch groove
9a First notch groove
9b Second notch groove

Claims (5)

An oil suction port, an oil discharge port, and a casing having an internal space communicating with the oil suction port and the oil discharge port;
An outer rotor having a predetermined number of teeth, which is rotatably accommodated in the internal space;
The external teeth that mesh with the inner teeth of the outer rotor from the inside are one less than the number of teeth of the inner teeth, and are accommodated inside the outer rotor so as to be rotatable around an axis that is eccentric to the outer rotor, An oil pump comprising an inner rotor that forms a plurality of confinement portions with the outer rotor,
A predetermined gap is provided between the end portion of the oil suction port and the start end portion of the oil discharge port,
A notch groove that communicates with the oil discharge port is formed on one inner peripheral surface in the axial direction in which the outer rotor slides, which forms the internal space of the casing,
The notch groove includes a first notch groove that communicates with the closed portion when the single closed portion rotates a predetermined pitch from the stage where the suction stroke is completed, and the first notch groove that is continuous with the first notch groove. A depth of at least two stages including a second notch groove deeper than the notch groove and shallower than the depth of the oil discharge port;
The first notch groove has a depth of 0.8% to 2.0% with respect to the thickness of the outer rotor,
The oil pump according to claim 2, wherein the second notch groove has a depth of 4.0% to 35% with respect to a thickness of the outer rotor. The oil pump according to claim 1, wherein
The notch groove is formed on an inner peripheral surface opposite to the inner peripheral surface on which the oil discharge port is formed, of the inner peripheral surface in the axial direction in which the outer rotor slides, which forms the inner space of the casing. And an oil pump configured to communicate with the oil discharge port via the closing portion. The oil pump according to claim 1 or 2,
Immediately before the closed portion communicates with the oil discharge port, the area of the region where the first notch groove communicates with the closed portion in plan view is 0.2 times the area of the closed portion. An oil pump characterized by being 0.4 times or less. In the oil pump according to any one of claims 1 to 3,
As one of the confining portions rotates toward the oil discharge port, the area of the region where the first notch groove and the confining portion communicate with each other in plan view gradually increases with respect to the area of the confining portion. An oil pump characterized by being configured to be large. In the oil pump according to any one of claims 1 to 4,
The first notch groove communicates with the confinement portion at a position advanced from 0.02 to 0.06 times the pitch of the internal teeth from the stage where one confinement portion has finished the suction stroke. An oil pump characterized by being formed.

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