JP2006002852A - Engine balancer device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an engine balancer device capable of avoiding flowing-out of lubricating oil and lubricating a journal part sufficiently. <P>SOLUTION: This balancer device provided in an engine rotatably to cancel vibration of the engine has a balance shaft driven by rotation of the engine, a counterweight part provided on the balance shaft to cancel vibration of the engine by rotating in accordance with rotation of the engine, a journal receiving part for receiving the balance shaft, a lubricating oil supply part opened in the journal receiving part, and the journal part provided in a section corresponding to the journal receiving part in the balance shaft, provided so that the weight of a side opposite to the counterweight part in the peripheral direction is lighter than the weight of a counterweight side, and provided to block at least a part of the lubricating oil supply part. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a balancer device that cancels vibrations of an engine.

2. Description of the Related Art Conventionally, in an engine balancer device, ribs that connect both perfect circular contour portions are provided at both axial end portions of a journal portion in order to reduce the size of the counterweight portion (see, for example, Patent Document 1).
JP 2001-140985 A (see FIG. 6)

  However, in the above prior art, a lubricating oil supply part for supplying lubricating oil to the journal part is provided at a position corresponding to the concave part in the journal part. As a result, there was a problem that the journal part could not be sufficiently lubricated.

  The present invention has been made paying attention to the above problems, and an object of the present invention is to provide an engine balancer device capable of avoiding outflow of lubricating oil and sufficiently lubricating a journal portion.

  In order to achieve the above object, in the present invention, in a balancer device that is rotatably provided in the engine and cancels vibrations of the engine, the balance shaft that is driven by the rotation of the engine is provided on the balance shaft, A counterweight portion that counteracts vibrations of the engine by rotating with the rotation of the engine, a journal receiving portion that supports the balance shaft, a lubricating oil supply portion that opens to the journal receiving portion, and a balance shaft Provided at a portion corresponding to the journal receiving portion, provided so that the counterweight portion and the opposite side in the circumferential direction are lighter than the counterweight side, and provided to block at least a part of the lubricating oil supply portion The journal part was decided to have.

  Therefore, it is possible to provide an engine balancer device that can avoid the outflow of lubricating oil and sufficiently lubricate the journal portion.

  DESCRIPTION OF THE PREFERRED EMBODIMENTS The best mode for realizing an engine balancer device of the present invention will be described below based on Embodiments 1 to 4 shown in the drawings.

[Configuration of balancer device]
(Front view)
Example 1 will be described with reference to FIGS. FIG. 1 is a front view of an engine equipped with a balancer device 10 according to the first embodiment. FIG. 1 shows a cross-sectional view of only the oil pan portion to which the balancer device 10 is attached. The engine 1 includes a head cover 2, a cylinder head 3, a cylinder block 4, a lower block 5, a crankshaft 6, a crankshaft sprocket 7, and an oil pan 8. A balancer device 10 is placed in an oil pan 8 below the lower block 5. It is stored and fastened to the lower block 5 with bolts B.

  The balancer device 10 has two first and second balance shafts 100 and 200 inside the housing 300, and a balancer sprocket 110 is provided at one end of the first balance shaft 100. The balancer sprocket 110 is connected to the crankshaft sprocket 7 of the engine 1 via the chain 12 and has a mechanism for rotating the first balance shaft 100 as the crankshaft 6 rotates. The chain 12 is provided with a tensioner 13 to adjust the tension of the chain 12.

(Axial partial sectional view)
FIG. 2 is a partial cross-sectional view in the direction of the crankshaft 6 of the engine 1 provided with the balancer device 10, and shows a cross section taken along the line AA in FIG. 3 is a partial cross-sectional view of the balancer device 10, and FIG. 4 is a top view of the balancer device 10 when the upper housing 301 is removed. In FIG. 2, only the crankshaft 6 and the first balance shaft 100 are side views. Both the first and second balance shafts 100 and 200 are provided so that their axes are parallel to the x-axis which is the axial direction of the crankshaft 6 of the engine 1. In the figure, the y-axis indicates the vertical movement direction of the piston, not shown.

  The first balance shaft 100 is provided with a balancer sprocket 110, a first journal portion 120, a first helical gear 130, a first counterweight portion 140, a second journal portion 150, and a second counterweight portion 160 in order from the negative x-axis direction. ing. The first and second journal portions 120 and 150 are rotatably supported by first and second journal receiving portions 310 and 320 provided in the housing 300, respectively.

  Although not shown in FIG. 2, the second balance shaft 200 is substantially the same member as the first balance shaft 100 and is different from the first balance shaft 100 only in that the balancer sprocket 110 is not provided. The second balance shaft 200 is provided with a third journal portion 220, a second helical gear 230, a third counterweight portion 240, a fourth journal portion 250, and a fourth counterweight portion 260 in order from the x-axis negative direction.

  Similar to the first balance shaft 100, the second balance shaft 200 is rotatably supported by third and fourth journal receiving portions 330 and 340 provided in the housing 300 in the third and fourth journal portions 220 and 250, respectively. In addition, the first and second helical gears 130 and 230 of the first balance shaft 100 and the second balance shaft 200 are provided in the housing 300 so as to mesh with each other. Therefore, the rotation of the crankshaft 6 is transmitted to the first balance shaft 100 via the chain 12 and further transmitted to the second balance shaft 200 via the first and second helical gears 130 and 230.

  The first and second counterweight portions 140 and 160 are semi-cylindrical members, and extend from the first and second counterweight portion planes 141 and 161, which are planes passing through the center of the first balance shaft 100, to the circumference on one side. Is provided. The centroids G1 and G2 of the first and second counterweight portions 140 and 160 are eccentric with respect to the axis of the first balance shaft 100, and a straight line connecting the centroids G1 and G2 is provided so as to be parallel to the x axis. It has been.

  Similar to the first balance shaft 100, the third and fourth counterweight portions 240 and 260 of the second balance shaft 200 are also formed in the same manner as the first balance shaft 100, and the third and fourth counterweight portions 240 and 260 are formed. Centroids G3 and G4 are eccentric with respect to the axis of the second balance shaft 200, and a straight line connecting the centroids G3 and G4 is provided parallel to the x-axis. Therefore, the center of gravity G1, G2, G3, G4 of each counterweight part exists on a plane N parallel to the x axis and perpendicular to the y axis. The plane N is parallel to the xz plane formed by the x axis shown in FIG. 2 and the z axis shown in FIG.

  Furthermore, G100, which is the center of gravity of the first balance shaft 100, which is the combined center of gravity of the center of gravity G1, G2 of the first and second counterweight portions 140, 160, and the center of gravity G3 of the third, fourth counterweight portions 240, 260 G200, which is the center of gravity of G4 and the center of gravity of second balance shaft 200, is eccentric with respect to the center of each shaft. When assembled, the first and second helical gears 130 and 230 are meshed so that the centers of gravity G100 and G200 are symmetric with respect to the y-axis.

[Engine damping by rotation of balance shaft]
The rotation of the crankshaft 6 is transmitted to the first balance shaft 100 via the chain 12 and further transmitted to the second balance shaft 200 via the first and second helical gears 130 and 230. Since the center of gravity G100, G200 of the first and second balance shafts 100, 200 is eccentric with respect to the rotation shaft, a vibration force is generated in the first, second balance shafts 100, 200 with rotation. At this time, since the first and second balance shafts 100 and 200 are directly meshed with each other in the first and second helical gears 130 and 230, they rotate in opposite directions.

  At this time, the centroids G100 and G200 of the first and second balance axes 100 and 200 are symmetric with respect to the y axis, that is, on a plane N parallel to the xz plane, and rotate in opposite directions. In the z-plane direction, that is, the z-axis direction, the excitation forces of the first and second balance shafts 100 and 200 cancel each other, and the resultant force of the excitation force is generated only in the y-axis direction.

  Accordingly, the first and second phases are such that the phase of the resultant force of the first and second balance shafts 100 and 200 in the y-axis direction is opposite to the phase of the exciting force due to the vertical movement of the piston. 2 By decentering the counterweight portions 140 and 160, the vibration of the piston is canceled and the engine 1 is damped.

[Details of balancer device]
(Axial partial sectional view)
The details of the partial cross section of the balancer device 10 will be described with reference to FIG. Like FIG. 2, FIG. 3 shows the AA cross section in FIG. 1, and only the first balance shaft 100 is a side view. A housing 300 of the balancer apparatus 10 includes an upper housing 301 and a lower housing 302, and an oil passage 350 that supplies lubricating oil to the first and second journal receiving portions 310 and 320 is provided between the upper housing 301 and the lower housing 302. It has been. Lubricating oil is supplied to the first and second journal receiving portions 310 and 320 through the first and second lubricating oil supply holes 311 and 321 by the oil passage 350.

  A plurality of the first and second lubricating oil supply holes 311 and 321 are provided in the inner peripheral radial direction center of the first and second journal receiving portions 310 and 320. In addition, first and second lubricating oil supply grooves 312 and 322 are provided over the entire circumference in the inner radial direction central portion of the first and second journal receiving portions 310 and 320, and the first and second lubricating oil supply holes are provided. Reference numerals 311 and 321 open in the first and second lubricating oil supply grooves 312 and 322, and the lubricating oil flows through the first and second journal receiving portions 310 and 320 through the first and second lubricating oil supply grooves 312 and 322. Supplied around the lap.

  The first balance shaft 100 has a shaft shape in the first journal portion 120, but in the second journal portion 150, the bearing portion opposite to the circumferential same side bearing portion 152 of the first and second counterweight portions 140 and 160. 151, the circumferentially opposite bearing portion 151 is provided with a narrower axial width than the circumferentially identical bearing portion 152, and thus the circumferentially opposite bearing portion 151 is more than the circumferentially identical bearing portion 152. Is also lightweight. That is, in the second journal portion 150, the circumferential same side bearing portion 152 contacts over the entire length in the axial direction of the second journal receiving portion 320, but the circumferential opposite side bearing portion 151 is the center in the axial direction of the second journal receiving portion 320. Touch only at the part.

  The circumferentially opposite bearing portion 151 of the second journal portion 150 is provided so that the axial width completely closes the second lubricating oil supply groove 322 of the second journal receiving portion 320. Accordingly, the lubricating oil supplied from the second lubricating oil supply hole 321 is always supplied to the entire circumference of the sliding surface of the second journal part 150 and the second journal receiving part 320 via the second lubricating oil supply groove 322. It becomes.

  In addition, between the x-axis positive direction end surface 154 of the circumferentially opposite bearing portion 151 of the second journal portion 150 and the second counterweight portion plane 161 of the second counterweight portion 160, A first rib 153 is provided along the axis. In the second journal portion 150, the circumferential opposite side bearing portion 151 and the circumferential same side bearing portion 152 have different axial widths, and there is a concern that the strength is insufficient. Therefore, reinforcement is provided by providing the first rib 153. .

  Since the rotation of the first and second balance shafts 100 and 200 is transmitted by the first and second helical gears 130 and 230, the first and second balance shafts 100 and 200 are thrust in the axial direction along with the rotation. Generate power. Therefore, first and second thrust receiving portions 131 and 132 are provided on both end surfaces in the x-axis direction of the first helical gear 130, and contact and slide with the thrust surfaces 302 a and 302 b of the lower housing 302. The axial movement of the is restricted.

  The first and second thrust receiving portions 131 and 132 are supplied with lubricating oil leaked through lubrication of the entire circumference of the sliding surfaces of the second journal portion 150 and the second journal receiving portion 320. The thrust receivers 131 and 132 are lubricated.

  The second balance shaft 200 is the same as the first balance shaft 100 except that the balancer sprocket 110 is not provided as described above. Also in the housing 300, the third journal receiving unit 330 corresponds to the first journal receiving unit 310, and the fourth journal receiving unit 340 has the same configuration and function corresponding to the second journal receiving unit 320. The same applies to other configurations.

(Top view)
A top view of the balancer device 10 when the upper housing 301 is removed will be described with reference to FIG. As described above, the second rib 253 is provided on the fourth journal portion 250 of the second balance shaft 200, similarly to the second journal portion 150 of the first balance shaft 100. Further, the lubricating oil is supplied to the first to fourth journal receiving portions 310 to 340 through the first and second lubricating oil supply holes 311 and 321 by the oil passage 350 provided between the upper housing 301 and the lower housing 302. To do.

  Similar to the first and second lubricating oil supply holes 311 and 321, the third and fourth lubricating oil supply grooves 332 and 342 are formed over the entire circumference in the inner radial direction central portions of the third and fourth journal receiving portions 330 and 340. The third and fourth lubricating oil supply grooves 332 and 342 are provided with a plurality of third and fourth lubricating oil supply holes 331 and 341, and the lubricating oil is supplied from the first to fourth lubricating oil supply grooves 312 to 3-12. 342 is supplied to the entire circumference of the first to fourth journal receivers 310 to 340.

  Similarly to the second journal portion 150, the circumferentially opposite bearing portions 251 of the third and fourth counterweight portions 240 and 260 in the fourth journal portion 250 have a width in the axial direction larger than the circumferentially identical side bearing portion 261. Narrow and light weight. Further, the circumferentially opposite bearing portion 251 is provided such that the axial width completely closes the fourth lubricating oil supply groove 342 of the fourth journal receiving portion 340.

  Therefore, like the second journal receiving portion 320, the lubricant supplied from the fourth lubricating oil supply hole 341 always slides between the fourth journal portion 250 and the fourth journal receiving portion 340 via the fourth lubricating oil supply groove 342. It will be supplied to the entire circumference of the moving surface. In addition, the second rib is formed along the axis of the second balance shaft 200 between the x-axis positive direction end surface 254 and the fourth counterweight portion plane 261 in the circumferentially opposite bearing portion 251 of the fourth journal portion 250. 253 is provided for reinforcement.

  Further, third and fourth thrust receiving portions 231 and 232 are provided on both end surfaces in the x-axis direction of the second helical gear 230, and contact and slide with the thrust surfaces 302 c and 302 d of the lower housing 302, so that the first balance shaft 100. The axial movement of

(Diameter sectional view)
FIG. 5 is a radial cross-sectional view of the balancer device 10. In FIG. 5, the BB cross section in FIG. 4 is shown. As described above, the lubricating oil from the oil passage 350 is supplied to the second and fourth journal receiving portions by the second and fourth lubricating oil supply holes 321 and 341 provided in the second and fourth lubricating oil supply grooves 322 and 342. 320 and 340 are supplied to the entire circumference.

  Further, the circumferentially opposite bearing portions 151 and 251 in the second and fourth journal portions 150 and 250 are provided with a narrower axial width than the circumferentially identical bearing portions 162 and 262. Further, the circumferentially opposite bearing portions 151 and 251 are provided so that the axial width thereof completely closes the second and fourth lubricating oil supply grooves 322 and 342 of the second and fourth journal receiving portions 320 and 340, Lubricating oil is always supplied to the entire circumference of the sliding surfaces of the second and fourth journal portions 150 and 250 and the second and fourth journal receiving portions 320 and 340.

  Furthermore, the lubricating oil supplied to the sliding surface is also introduced into the inter-journal oil passage 351, and the lubricating oil is ensured by supplying the lubricating oil to the second and fourth journal receiving portions 320 and 340.

[Contrast of effects of conventional example and first embodiment]
FIG. 6 is a diagram comparing the perspective view of the balance shaft in the conventional example and the first embodiment of the present application. FIG. 6A shows the balance axis of the conventional example, and FIG. 6B shows the first balance axis 100 of Example 1 of the present application. As shown in FIG. 6 (a), in the conventional balancer device for an engine, in order to reduce the size of the counterweight portions 140 ′ and 160 ′, both circular contour portions 151 ′ are formed at both axial ends of the journal portion 150 ′. In the above prior art, a lubricating oil supply part for supplying lubricating oil to the journal part 150 'is provided at a position corresponding to the concave part 153' in the journal part. Therefore, the lubricating oil flows out from the recess 153 ′, and it becomes difficult to supply the lubricating oil to the journal portion 150 ′, and there is a problem that the journal portion 150 ′ cannot be sufficiently lubricated.

  In addition, since the journal portion 150 ′ is located upstream in the lubricant supply of the balancer device, if the journal portion 150 ′ flows out of the journal portion 150 ′, it is difficult to sufficiently supply the lubricant to the downstream side. There is also.

  On the other hand, in the first embodiment of the present application, the first, second or third, fourth counterweight portions 140, 160 or 240, 260 are provided at portions corresponding to the second and fourth journal receiving portions 320, 340. The circumferentially opposite bearing portions 151 and 251 on the opposite sides in the circumferential direction are provided so as to be lighter than the counterweight sides, and the circumferentially opposite bearing portions 151 and 251 in the second and fourth journal portions 150 and 250 are provided. The width of the second and fourth lubricating oil supply grooves 322 and 342 can be always completely closed.

  As a result, since the circumferentially opposite bearing portions 151 and 251 on the shafts of the first and second balance shafts 100 and 200 are lighter than the counterweight side, the eccentric amount of the first and second balance shafts 100 and 200 and Each counterweight part can be reduced in weight and size without suppressing the excitation force at the time of rotation. Further, the second and fourth lubricating oil supply grooves 322 and 342 are always completely closed, so that the lubricating oil can be prevented from flowing out. By sufficiently supplying the lubricating oil to the downstream side, sufficient lubrication of the journal portion can be achieved. (Corresponding to claim 1).

  Further, by providing the circumferentially opposite bearing portions 151 and 251 with a width that can completely block the second and fourth lubricating oil supply grooves 322 and 342, the second and fourth journal portions 150 and 250 2. The fourth lubricating oil supply grooves 322 and 342 are always completely closed, and the second and fourth journal portions 150 and 250 and the second and fourth journal receiving portions 320 and 340 can be constantly lubricated. Thus, the lubrication effect of the journal portion can be further improved (corresponding to claim 2).

  Further, the circumferentially opposite bearing portions 151 and 251 in the second and fourth journal portions 150 and 250 are provided with a narrower axial width than the circumferentially identical bearing portions 162 and 262, thereby further improving the above-described effects. This can be improved (corresponding to claim 3).

  A second embodiment will be described with reference to FIG. Since the basic configuration is the same as that of the first embodiment, only different points will be described. FIG. 7 is a partial sectional view in the axial direction of the balancer device 10 according to the second embodiment. Also in the second embodiment, since the configuration other than the balancer sprocket 110 provided on the first balance shaft 100 is the same for both the first and second balance shafts 100 and 200, only the first balance shaft 100 will be described. In the first embodiment, one oil passage 350 is provided, and the second lubricating oil supply groove 322 is closed by the circumferentially opposite bearing portion 151 that is a bearing portion on the opposite side in the circumferential direction of the second journal portion 150 of the first balance shaft 100. To ensure lubrication.

  On the other hand, in the second embodiment, two oil passages 350a and 350b are provided, and the first and second circumferentially opposite bearing portions 151a and 151b, which are two bearing portions, are provided on the opposite side of the second journal portion 150 in the circumferential direction. Provided. The first and second circumferentially opposite bearing portions 151a and 151b close the two lubricating oil supply grooves 322a and 322b provided over the inner periphery of the second journal receiving portion 320a, thereby ensuring lubrication.

  In the second embodiment, the first rib 153a is provided between the first circumferentially opposite bearing portion 151a and the first counterweight portion plane 141, and the second circumferentially opposite bearing portion 151b and second counterweight portion plane 161 are provided. The second rib 153b is provided between the first balance shaft 100 and the first balance shaft 100 is reinforced by the two first and second ribs 153a and 153b.

  As a result, the second journal portion is supported by the first and second circumferentially opposite bearing portions 151a and 151b which are two bearing portions, and the first balance shaft 100 is supported by the two first and second ribs 153a and 153b. Therefore, the strength of the balance shaft can be sufficiently secured. In addition, in order to supply lubricating oil from the two oil passages 350a and 350b, more lubricating oil can be supplied, and when it is necessary to increase the vibration generating force of the balancer device such as a vehicle equipped with a large engine, By using the configuration of the second embodiment, the strength and lubricity of the journal portion can be secured at the same time.

  A third embodiment will be described with reference to FIG. Since the basic configuration is the same as that of the first embodiment, only different points will be described. FIG. 8 is a partial cross-sectional view in the axial direction of the balancer device 10 according to the third embodiment. Also in the third embodiment, since the configuration other than the balancer sprocket 110 provided on the first balance shaft 100 is the same for both the first and second balance shafts 100 and 200, only the first balance shaft 100 will be described. In the first embodiment, first and second thrust receiving portions 131 and 132 are provided on both end surfaces in the x-axis direction of the first helical gear 130, and contact and slide with the thrust surfaces 302 a and 302 b of the lower housing 302. Restricted the axial movement of.

  On the other hand, in Example 3, the semicircular first and second protrusions that protrude from the first and second counterweight part planes 141 and 161 over the circumference opposite to the first and second counterweight parts 140 and 160 are provided. Portions 143 and 163 are provided. The first and second protrusions 143 and 163, the x-axis positive direction end surface 142 of the first counterweight unit 140, and the x-axis negative direction end surface 162 of the second counterweight unit 160 have the x-axis of the second journal receiving unit 320. The first and second thrust receiving portions 323 and 324 which are both end surfaces in the direction are brought into contact with each other to receive the thrust force of the first balance shaft 100.

  As a result, both end surfaces in the x-axis direction of the second journal receiving portion 320 can be sufficiently lubricated, and the thrust force of the first and second helical gears 130 and 230 of the first and second balance shafts 100 and 200 can be increased. Even in this case, sufficient wear resistance can be ensured.

  Example 4 will be described with reference to FIG. Since the basic configuration is the same as that of the first embodiment, only different points will be described. FIG. 9 is a partial sectional view in the axial direction of the balancer device 10 according to the fourth embodiment. Also in the fourth embodiment, since the first and second balance shafts 100 and 200 are the same except for the balancer sprocket 110 provided on the first balance shaft 100, only the first balance shaft 100 will be described. In the first embodiment, the first and second journal receiving sections 310 and 320 support the first and second journal sections 120 and 150. In the fourth embodiment, in addition to this, the third journal section 170 and the third journal receiving section. 370 is provided, and the first balance shaft 100 is supported by three journal portions, and the counterweight portion is provided between the second and third journal portions 150 and 170.

  Thereby, it becomes possible to reduce the weight load of the 2nd journal receiving part 320 of the 1st balance shaft 100, and it can improve wear resistance.

[Other embodiments]
Although the best mode for carrying out the present invention has been described based on the first embodiment, the specific configuration of the present invention is not limited to each embodiment and does not depart from the gist of the present invention. Any changes in the design of the range are included in the present invention.

  Further, technical ideas other than the claims that can be grasped from the respective embodiments will be described below together with the effects thereof.

(A) In the engine balancer device according to claim 3,
The lubricating oil supply part in the journal receiving part is arranged in an intermediate part in the axial direction range of the journal receiving part, and the counterweight part in the journal part is positioned in the intermediate part in the range of the journal part. An engine balancer device.

  Lubricating oil is evenly supplied to the counterweight portion and both the counterweight portion and the circumferentially opposite side, so that the journal portion and the journal receiving portion are evenly worn and the performance of the bearing is not impaired.

(B) In the engine balancer device according to claim 3,
A balancer device for an engine, characterized in that a thrust receiving portion for preventing axial movement of the balance shaft is provided on at least one end side of the journal portion.

  Since the leaked lubricating oil is supplied to the thrust receiving portion, the thrust receiving portion can be sufficiently lubricated.

(C) In the engine balancer device according to claim 3,
A balancer device for an engine, wherein a rib is formed at least on one end side in the axial direction of the journal portion on the opposite side to the counterweight portion in the circumferential direction.

  The strength of the journal portion on the side opposite to the counterweight portion in the circumferential direction is improved.

(D) In the engine balancer device described in (c) above,
The balancer device for an engine, wherein the rib is formed along an axial direction of the balance shaft.

In the engine balancer device described in (d) above,
An engine balancer device comprising: a lubricating oil supply hole that opens to the inner periphery of the journal receiving portion; and an annular groove that is formed in an annular shape so as to communicate with the lubricating oil supply hole.

1 is a front view of an engine equipped with a balancer device in Embodiment 1. FIG. It is a crankshaft direction fragmentary sectional view of the engine which equipped with the balancer device in Example 1. FIG. It is a fragmentary sectional view of the balancer device in Example 1. It is a top view of the balancer device in Example 1. It is radial direction sectional drawing of the balancer apparatus in Example 1. FIG. It is a contrast figure of the perspective view of the balance shaft in a prior art example and this-application Example 1. FIG. It is an axial direction fragmentary sectional view of the balancer apparatus in Example 2. FIG. It is an axial direction fragmentary sectional view of the balancer apparatus in Example 3. FIG. It is an axial direction fragmentary sectional view of the balancer apparatus in Example 4.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 Balancer apparatus 100 1st balance shaft 110 Balancer sprocket 120 1st journal part 130 1st helical gear 140 1st counterweight part 141 1st counterweight part plane 142 x-axis positive direction end surface 150 2nd journal part 151 Circumferentially opposite bearing Portion 152 circumferential same side bearing portion 153 rib 154 x-axis positive direction end surface 160 second counter weight portion 161 second counter weight portion plane 162 x-axis negative direction end surface 200 second balance shaft 220 third journal portion 230 second helical gear 240 Third counterweight portion 242 x-axis positive direction end surface 250 Fourth journal portion 251 Circumferentially opposite bearing portion 252 Circumferentially same side bearing portion 253 Second rib 254 x-axis positive direction end surface 260 Fourth counterweight portion 261 Fourth counter Way Toe plane 262 x-axis negative direction end surface 300 Housing 301 Upper housing 302 Lower housing 310 First journal receiving portion 311 First lubricating oil supply hole 312 First lubricating oil supply groove 320 Second journal receiving portion 321 Second lubricating oil supply hole 322 Second lubricating oil supply groove 323 Second thrust receiving portion 330 Third journal receiving portion 331 Third lubricating oil supply hole 332 Third lubricating oil supply groove 340 Fourth journal receiving portion 341 Fourth lubricating oil supply hole 342 Fourth lubrication Oil supply groove 343 Third thrust receiving portion 344 Fourth thrust receiving portion 350 Oil passage 351 Inter-journal oil passage

Claims (3)

In the balancer device that is rotatably provided in the engine and for canceling the vibration of the engine,
A balance shaft driven by rotation of the engine;
A counterweight portion provided on the balance shaft and counteracting vibrations of the engine by rotating with rotation of the engine;
A journal receiving portion for bearing the balance shaft;
A lubricating oil supply section opening in the journal receiving section;
Provided at a portion corresponding to the journal receiving portion, provided so that the counterweight portion and the opposite side in the circumferential direction are lighter than the counterweight side, and provided to block at least a part of the lubricating oil supply portion Journal portion of the balance shaft
An engine balancer device comprising: The engine balancer device according to claim 1,
The engine balancer device is characterized in that the journal portion is provided so as to always completely cover the lubricating oil supply portion. The engine balancer device according to claim 1,
A balancer device for an engine, characterized in that a side of the journal portion opposite to the counterweight portion in the circumferential direction is formed narrower than the counterweight portion side.

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