JP2018076929A - bearing - Google Patents

Abstract

A bearing for adjusting the flow of lubricating oil based on a change in temperature of the lubricating oil flowing between a rotating shaft and the bearing is provided. An oil supply hole for supplying lubricating oil supplied from an oil supply passage formed in a cylinder block to the rotating shaft side, and an oil supply groove that communicates with the oil supplying hole and faces the rotating shaft, Is provided in the oil supply groove 14 and in the oil supply groove 14, and is supplied to the oil supply groove 14 from the oil supply hole 13 corresponding to the temperature of the lubricating oil flowing through the oil supply groove 14. A heat-sensitive flow rate control valve 20 that adjusts the flow rate of oil is configured. [Selection] Figure 2

Description

  The present invention relates to a bearing that holds a rotating shaft such as a crankshaft.

  A rotating shaft such as a crankshaft of the engine is supported by, for example, a bearing shown in FIG. This bearing 100 is configured by abutting the ends of two split bearings 101 and 102 (hereinafter referred to as upper metal 101 and lower metal 102) made of a metal plate having a semicircular cross section. This bearing 100 is incorporated in the cylinder block 2 of the engine. The cylinder block 2 is provided with an oil supply passage 3 that sends out the lubricating oil sent from an oil pump (not shown), and an oil groove 4 that communicates with the oil supply passage 3 and distributes the lubricating oil along the outer periphery of the bearing 100. Is formed.

  The upper metal 101 is formed with an oil supply hole 103 for supplying the lubricating oil supplied through the oil supply passage 3 and the oil groove 4 to the rotary shaft 1 and an oil supply groove 104 communicating with the oil supply hole 103 and facing the rotary shaft 1. Has been. Lubricating oil is supplied between the upper metal 101 and the rotary shaft 1 through the oil supply hole 103 and the oil supply groove 104. The upper metal 101 and the lower metal 102 are fastened together in a state where pressure is applied in the abutting direction. At this time, the upper metal 101 and the lower metal 102 are both deformed into a flat shape by this pressure (see FIG. 3), and a gap g is formed between the upper metal 101 and the lower metal 102 and the rotating shaft 1 in the vicinity of the mating portion. Arise. Through this gap g, the lubricating oil supplied to the upper metal 101 side flows to the lower metal 102 side (see the arrow in FIG. 3) along with the rotation of the rotating shaft 1 (see the white arrow in FIG. 3). The entire periphery of the rotary shaft 1 is lubricated by the lubricating oil.

  Lubricating oil varies greatly in fluidity depending on its temperature. For this reason, in the bearing 100 having no flow rate adjusting mechanism as shown in FIG. 3, the amount of lubricating oil supplied to the bearing 100 is low when the temperature of the lubricating oil is low and the fluidity is low just after the engine is started. On the other hand, when the temperature of the lubricating oil rises sufficiently after the engine starts and the fluidity is high, there may be a problem that the supply of lubricating oil becomes excessive and the stirring resistance increases.

  Therefore, for example, in the rolling bearing described in Patent Document 1, an oil supply passage for supplying the lubricating oil to the housing supporting the bearing is formed, and a bypass groove communicating with the oil supply passage is formed on the outer peripheral surface of the outer ring. The bypass groove is provided with a temperature deformation member made of a shape memory alloy, bimetal, or the like. According to this configuration, when the temperature of the lubricating oil is low and its fluidity is low, the opening of the oil supply hole is increased, and the inflow of the lubricating oil to the outer ring side is promoted. On the other hand, when the temperature of the lubricating oil increases and its fluidity increases, the temperature deformation member is deformed and the opening of the oil supply hole is reduced. Due to the deformation of the temperature deformation member, the inflow of lubricating oil to the outer ring side is suppressed, and an increase in stirring resistance is prevented (see FIG. 5, paragraphs 0032 to 0034 of Patent Document 1).

JP 2014-109311 A

  In the configuration described in Patent Document 1, since the temperature deformation member is arranged on the upstream side of the bearing in the lubricating oil flow path, the temperature change of the lubricating oil before flowing into the bearing (on the bearing outer peripheral side) Deforms corresponding to. However, the lubricity of the lubricating oil is strongly influenced by the temperature change on the inner peripheral surface side of the bearing due to the frictional heat generated between the rotating shaft and the bearing. There is a problem that it is difficult to adjust the flow rate of the lubricating oil based on the temperature change. Further, when the temperature of the lubricating oil is low and the fluidity is low, the inflow of the lubricating oil is promoted, which causes a problem that the frictional resistance between the bearing and the rotating shaft is increased.

  Accordingly, an object of the present invention is to adjust the flow of the lubricating oil based on the temperature change of the lubricating oil flowing between the rotating shaft and the bearing.

  In order to solve the above-mentioned problems, in the present invention, an oil supply hole that supplies lubricating oil supplied from an oil supply passage formed in a cylinder block to the rotary shaft side, and communicates with the oil supply hole and faces the rotary shaft. An oil supply groove is formed, and is provided in the oil supply groove with a bearing body that supports the rotating shaft, and is supplied from the oil supply hole to the oil supply groove in accordance with the temperature of the lubricating oil flowing in the oil supply groove. And a heat sensitive flow control valve for adjusting the flow rate of the lubricating oil.

  In the said structure, it is preferable to comprise the said bearing main body from the division | segmentation bearing divided | segmented to radial direction.

  In this configuration, it is preferable that the heat-sensitive flow rate control valve has a temperature characteristic that is deformed so as to increase the flow rate as the temperature increases.

  In the configuration employing the heat sensitive flow control valve having the above temperature characteristics, the maximum displacement in the radial direction of the rotating shaft of the heat sensitive flow control valve is the depth of the oil supply groove and the maximum displacement. It can be set as the structure smaller than the sum of the magnitude | size of the clearance gap between the said bearing main body and the said rotating shaft in the circumferential direction position. Alternatively, the heat sensitive flow control valve includes a bearing body at a circumferential position where the maximum displacement in the radial direction of the rotary shaft of the heat sensitive flow control valve is the depth of the oil supply groove and the maximum displacement. A stopper member that restricts to be smaller than the sum of the gaps between the rotating shaft and the rotating shaft can also be provided.

  Moreover, in the structure which employ | adopted the heat sensitive flow control valve which has said temperature characteristic, the said oil supply hole is formed in multiple numbers, and each said oil supply hole is provided with the said heat sensitive flow control valve, and it is close to the said oil supply path. The heat-sensitive flow control valve on the side can be configured to operate at a higher temperature than the heat-sensitive flow control valve on the side far from the oil supply passage.

  In each of the above-mentioned configurations, it is preferable that the thermal flow rate control valve is made of a bimetal or a shape memory alloy.

  In each said structure, it is preferable to set it as the structure which the opening-and-closing side edge part of the said thermosensitive flow control valve is facing the rotation direction side of the said rotating shaft.

  The bearing according to the present invention is provided with a heat-sensitive flow rate adjustment valve in an oil supply groove formed in the bearing body, and the lubricant oil supplied to the oil supply groove from the oil supply hole formed in the bearing body by the heat-sensitive flow rate adjustment valve. The flow rate of was adjusted. In this way, by providing a heat-sensitive flow control valve in the oil supply groove, the flow rate of the lubricating oil can be adjusted quickly in response to a temperature change caused by frictional heat generated between the rotating shaft and the bearing. Thus, seizure between the rotating shaft and the bearing and friction loss can be reliably prevented.

Sectional drawing which shows one Embodiment of the bearing which concerns on this invention It is sectional drawing which shows the principal part of FIG. 1, Comprising: (a) at the time of the minimum flow (at the time of low temperature), (b) at the time of the maximum flow (at the time of high temperature) The bearing which concerns on a prior art is shown, (a) is sectional drawing, (b) is sectional drawing which follows the bb line in (a).

  One embodiment of a bearing according to the present invention is shown in FIGS. 1 and 2 (a) and 2 (b). This bearing is a sliding bearing which is used to support a rotating shaft 1 such as an engine crankshaft and which is lubricated with lubricating oil. This bearing is incorporated in the cylinder block 2 of the engine. The cylinder block 2 is formed with an oil supply passage 3 for sending out the lubricating oil sent from an oil pump (not shown), and an oil groove 4 that communicates with the oil supply passage 3 and distributes the lubricating oil along the outer periphery of the bearing. Has been. This bearing has a bearing body 10 and a heat-sensitive flow rate control valve 20 (hereinafter abbreviated as a control valve 20) as main components.

  The bearing body 10 is a cylindrical member formed by molding a metal plate, and is composed of split bearings 11 and 12 (hereinafter, referred to as upper metal 11 and lower metal 12) that are divided into two in the radial direction. In the upper metal 11, oil supply holes 13 for supplying the lubricating oil supplied from the oil supply passage 3 formed in the cylinder block 2 to the rotary shaft 1 are formed in two places. An oil supply groove 14 that communicates with the oil supply hole 13 and faces the rotation shaft is formed on the inner surface side of the upper metal 11 along the circumferential direction of the inner surface of the upper metal 11. The oil supply groove 14 terminates before reaching the circumferential end of the upper metal 11 (the mating portion with the lower metal 12). The lower metal 12 is a member having the same shape as the upper metal 11, but is different from the upper metal 11 in that the oil supply hole 13 and the oil supply groove 14 are not formed. The rotating shaft 1 is supported by the inner surface of the bearing body 10 (upper metal 11 and lower metal 12) so as to be rotatable around the shaft.

  The upper metal 11 and the lower metal 12 are fastened to each other while being pressed in the abutting direction. At this time, the upper metal 11 and the lower metal 12 are both deformed into a flat shape by this pressing force, and a gap g is generated between the upper metal 11 and the lower metal 12 and the rotary shaft 1 in the vicinity of the mating portion (FIG. 1). Etc.) Through this gap g, the lubricating oil supplied to the upper metal 11 side flows to the lower metal 12 side with the rotation of the rotary shaft 1 (see the white arrow in FIG. 1) (see the arrow in FIG. 1). The entire periphery of the rotary shaft 1 is lubricated by the lubricating oil. The lubricating oil that has lubricated the rotary shaft 1 flows out from the axial end of the bearing body 10 (in the direction perpendicular to the paper surface in FIG. 1 and the like) and returns to an oil pan (not shown) that temporarily stores the lubricating oil. .

  As described above, it is preferable to configure the bearing body 10 with the upper metal 11 and the lower metal 12 because the assembly can be easily performed. However, an undivided cylindrical bearing body 10 can also be employed. Also, a split bearing having a split number of 3 or more can be employed.

  The control valve 20 is provided in the vicinity (two places) of the oil supply hole 13 in the oil supply groove 14 formed on the inner surface side of the upper metal 11. This control valve 20 is comprised with the bimetal which deform | transforms with a temperature change. The control valve 20 has a function of adjusting the flow rate of the lubricating oil supplied from the oil supply hole 13 to the oil supply groove 14 by opening and closing the oil supply hole 13 in accordance with the temperature of the lubricating oil flowing through the oil supply groove 14. doing. In this embodiment, the control valves 20 provided at two locations have the same temperature characteristics (if the temperature change of the lubricating oil is the same, the deformation amount is the same). The control valve 20 has a plate shape slightly curved in the circumferential direction so as to follow the curvature of the inner surface of the oil supply groove 14. One end portion (fixed side end portion) of the control valve 20 is fixed in the oil supply groove 14, and the other end portion (opening / closing side end portion) opposite to the one end portion is a rotating shaft corresponding to a temperature change. 1 can be freely displaced in the radial direction.

As described above, by providing the adjusting valve 20 in the oil supply groove 14, the flow rate of the lubricating oil can be quickly adjusted in response to the temperature change of the lubricating oil caused by the frictional heat between the rotating shaft 1 and the bearing body 10. Can be adjusted appropriately. In this embodiment, the flow rate of lubricating oil through the oil supply hole 13 at a low temperature while the minimum flow rate (see arrow f ₁ in FIG. 2 (a)), the lubricating oil through the oil supply hole 13 at a high temperature It employs a control valve 20 having a temperature characteristic that can be a maximum flow rate (see arrow f ₂ in FIG. 2 (b)) flow rate.

  By adopting the control valve 20 having the above temperature characteristics, supply of lubricating oil to the bearing is suppressed at a low temperature (during cold start). By suppressing the supply of the lubricating oil, the frictional heat generated by the friction between the rotating shaft 1 and the bearing body 10 is less likely to be taken away by the lubricating oil, and the heating of the lubricating oil by this frictional heat is promoted. When the lubricating oil is heated, its fluidity increases, and seizure between the rotating shaft 1 and the bearing body 10 and friction loss can be reliably prevented.

  In addition, as the material of the control valve 20, another material that changes in shape due to a temperature change, such as a shape memory alloy, may be employed instead of the bimetal.

  In this embodiment, the cover area of the opening of the oil supply hole 13 by the adjustment valve 20 is approximately halved at the minimum flow rate (when the valve is closed) (see FIG. 2A). This is merely an example, and the cover area of the control valve 20 can be changed as appropriate in consideration of the temperature characteristics of the control valve 20, the required flow rate of the lubricating oil, and the like.

  The control valve 20 is provided with a stopper member 21. The stopper member 21 has a base portion 21a fixed to the control valve 20, and a locking portion 21b that is formed radially outward from the base portion 21a and bent in the circumferential direction. The locking portion 21b of the stopper member 21 is locked to the edge of the oil supply hole 13 when the opening / closing side end of the control valve 20 is displaced by the maximum displacement amount due to the temperature change of the lubricating oil. (See FIG. 2 (b)). This locking restricts further displacement of the control valve 20 and prevents the opening / closing side end from contacting the rotary shaft 1.

The maximum amount of displacement, the depth d of the oil supply groove 14, than the sum of the magnitude g ₁ of the gap between the bearing body 10 (upper metal 11) and the rotary shaft 1 at the radial position where the the maximum displacement amount Is also determined to be smaller.

Instead of providing the stopper member 21, the maximum displacement amount of the opening / closing side end is the depth d of the oil supply groove 14, and the bearing body 10 (upper metal 11) and the rotating shaft at the radial position where the maximum displacement amount is obtained. The control valve 20 having a temperature characteristic that is smaller than the sum of the gap sizes g ₁ between the control valve 20 and 1 may be employed.

  The control valve 20 may be provided within an angle range of 45 degrees in the circumferential direction from the joint portion of the upper metal 11 and the lower metal 12, and preferably within an angle range of 15 degrees. This is because, within this angle range, the gap g between the upper metal 11 and the rotary shaft 1 is relatively large, and there is a low possibility that the opening / closing side end of the control valve 20 contacts the rotary shaft 1.

  In the control valve 20, the open / close side end portion faces the rotation direction side of the rotary shaft 1 with respect to the fixed side end portion fixed in the oil supply groove 14. By arranging the control valve 20 in this way, even if the open / close side end and the rotary shaft 1 are in contact, the open / close side end abuts against the outer peripheral surface of the rotary shaft 1 and the control valve 20 is damaged. The trouble that the rotating shaft 1 is damaged can be prevented.

  In the above embodiment, the control valves 20 provided at two locations have the same temperature characteristics. For example, the control valve 20 on the side closer to the oil supply passage 3 is connected to the oil supply passage 3. It is also possible to employ a control valve 20 having different temperature characteristics, such as having a temperature characteristic that operates at a higher temperature than the far-side control valve 20. In this way, while the bearing body 10 is still in a low temperature state, the lubricating oil is prevented from being excessively supplied from the oil supply hole 13 close to the oil supply path 3, and the oil supply hole 13 far from the oil supply path 3 is preferentially used. Lubricating oil can be supplied to effectively suppress friction between the rotating shaft 1 and the bearing body 10.

  The bearing described above is merely an example, and as long as the problem of the present invention of adjusting the flow of the lubricating oil based on the temperature change of the lubricating oil flowing between the rotating shaft 1 and the bearing can be solved. For example, the position and number of the oil supply holes 13 formed in the bearing body 10 (upper metal 11), the formation range of the oil supply groove 14 in the circumferential direction, the shape and temperature characteristics of the heat-sensitive flow control valve 20 are appropriately changed. be able to.

1 Rotating shaft 2 Cylinder block 3 Oil supply path 4 Oil groove 10 Bearing body 11 Upper metal (split bearing)
12 Lower metal (split bearing)
13 Oil supply hole 14 Oil supply groove 20 Heat-sensitive flow rate control valve 21 Stopper member d Oil supply groove depth g ₁ Size of gap

Claims (8)

An oil supply hole for supplying the lubricating oil supplied from the oil supply passage formed in the cylinder block to the rotation shaft side and an oil supply groove that communicates with the oil supply hole and faces the rotation shaft are formed to support the rotation shaft. A bearing body;
A heat-sensitive flow rate control valve that is provided in the oil supply groove and adjusts the flow rate of the lubricating oil supplied from the oil supply hole to the oil supply groove in accordance with the temperature of the lubricating oil flowing in the oil supply groove;
Bearings.   The bearing according to claim 1, wherein the bearing main body is constituted by a divided bearing divided in a radial direction.   The bearing according to claim 2, wherein the heat-sensitive flow rate control valve has a temperature characteristic that is deformed so as to increase the flow rate as the temperature increases.   The maximum displacement in the radial direction of the rotary shaft of the thermal flow control valve is the depth of the oil supply groove and the size of the gap between the bearing body and the rotary shaft at the circumferential position where the maximum displacement is obtained. The bearing according to claim 3, wherein the bearing is smaller than the sum.   In the thermal flow control valve, the bearing body and the rotation at the circumferential position where the maximum displacement in the radial direction of the rotary shaft of the thermal flow control valve is the depth of the oil supply groove and the maximum displacement. The bearing according to claim 3, further comprising a stopper member that regulates to be smaller than a sum of a gap between the shaft and the shaft.   A plurality of the oil supply holes are formed, and each of the oil supply holes is provided with the heat-sensitive flow rate control valve, and the heat-sensitive flow rate control valve on the side closer to the oil supply passage is connected to the heat-sensitive flow rate adjustment valve on the side farther from the oil supply passage. The bearing according to any one of claims 3 to 5, wherein the bearing operates at a higher temperature than the valve.   The bearing according to any one of claims 1 to 6, wherein the heat-sensitive flow control valve is made of a bimetal or a shape memory alloy.   The bearing according to any one of claims 1 to 7, wherein an opening / closing side end portion of the heat-sensitive flow rate control valve faces a rotation direction side of the rotation shaft.

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