JPH0248668Y2 - - Google Patents

Description

[Detailed description of the invention] (Field of industrial application) This invention is a balancer and water pump installation in which a water pump is attached to one end of a balancer shaft, and both ends of the balancer shaft are rotatably supported. It's about structure.

(Prior Art) Conventionally, in order to reduce the vibration of the entire engine by canceling as much as possible the centrifugal force generated by the rotating parts in the engine, the inertial force of the reciprocating parts, and the various forces accompanying these, A balancer shaft is installed on the rotation axis. In addition, in the case of a water-cooled engine, there is a built-in water pump that is driven by the engine, and if these were driven individually, the number of parts would increase and the structure would be complicated and large. In order to improve this, it is known that a water pump is provided at one end of a rotating shaft coaxial with the balancer, and the balancer and water pump are rotationally driven on the same axis. (Utility Model Application No. 59-43627) Furthermore, both ends of the balancer shaft are rotatably supported by bearings, and it is necessary to supply lubricating oil to these bearings. In order to achieve simplification and downsizing, it is known that lubricating oil is supplied to both of the bearings through an oil hole formed in the balancer shaft and extending in the axial direction. There is. (Utility Model Application No. 57-35404) However, according to the former configuration, the balancer and
The balancer shaft that rotationally drives the water pump is separate, and the drive systems for the balancer and this balancer shaft are also separate systems, so the number of parts increases and the structure becomes more complicated and larger. Moreover, two lubrication systems are required to supply lubricating oil to the separate balancer and balancer shaft bearings, and even if the latter lubrication method is adopted, the number of parts in the entire engine system will be reduced. The increase in the size, complexity of the structure, and increase in size were unavoidable.

(Purpose of the invention) This invention was made in view of the above circumstances.
It is an object of the present invention to provide a mounting structure for a balancer and a water pump that can reduce the number of parts, simplify and downsize the structure, and achieve light engine drive.

(Structure of the invention) The mounting structure of the balancer and water pump according to this invention is such that bearing parts are set on mutually opposing bearing walls formed on both sides of the crankcase, and the balancer is fixed to the outer periphery of the balancer shaft at both ends. A pump impeller is rotatably supported by the bearing part, a pump impeller is detachably fixed to one end of the balancer shaft, and an oil passage communicating with each of the bearing parts is formed in the axial center of the balancer shaft. , characterized in that the oil supply passage formed in the bearing wall is communicated with the oil passage hole of the balancer shaft.

According to the above configuration, since the balancer and the pump impeller are integrally fixed to the balancer shaft,
Even one system can drive the balancer and water pump. In addition, since the drive system for the balancer and water pump is one system, there is only one lubrication system for supplying lubricating oil to the bearing of the balancer shaft, which reduces the number of parts in the entire engine system and improves the structure. Simplification and miniaturization can be achieved, and light engine drive can be achieved.

(Example) Hereinafter, an example of this invention will be described with reference to the drawings.

Figure 1 shows the engine E mounted on a motorcycle.
This is an example of FIG. In this Fig. 1, the section above X-X is a vertical cross-sectional front view of the side of engine E, and the section below X-X is from the front crankshaft B to the countershaft C installed at the rear. A bottom view of the horizontal dividing plane XX taken as a cross section (end surface) is shown. In addition, Fig. 2 shows the engine E along the dividing plane XX (Fig.
This is a drawing of the right side of the machine, viewed from the bottom. Here, the shafts A, B, and C are arranged in the order ABC from the front when viewed from the right side of the engine E. Note that a power take-off shaft that receives power from the countershaft C is not shown.

In FIG. 1, a crankcase 2 divided along the line X-X is provided at the bottom of a cylinder 1 provided at the top of an engine E. In this case, an upper main body 3 and a lower main body (not shown) are provided. It is formed by tightening with a vertical bolt (not shown) passed through the tightening bolt hole 5.

The upper and lower split type crankcase 2 has bearing walls 6, 6 on the right side R and the left side, respectively (see Fig. 2).
is formed. This bearing wall 6 is integral with the upper body 3 and the lower body, and is divided into upper and lower parts (tightened) by the bearing walls 6 from above and below.

Side covers 7, which are integral lids, are removably attached to both sides of the crankcase 2, and FIG. 1 shows the one on the right side of the engine E.

On the other hand, as shown in FIG. 2, the crankshaft B is supported at two axially intermediate locations (one of which is shown in the drawing) by an upper and lower split type intermediate bearing wall 8, and at both axial ends. is supported by the outer bearing wall 6. In FIG. 1, one end b thereof is shown.

C is a countershaft, which is arranged parallel to the rear position of the crankshaft B when viewed from the whole engine E, and this countershaft C has a bearing wall 6 corresponding to the right side of the engine E, as shown in FIG.
Both ends are supported by a bearing wall 6 provided on the left side of the engine E (left side in the drawing).

Reference numeral 9 in FIG. 1 denotes a transmission gear, which is arranged on the countershaft C. On the other hand, a clutch 10 is disposed at the left end of the countershaft C in the drawing. This clutch 10 has a driven housing 11 attached to a countershaft C, a drive housing 12 rotatably provided to the countershaft C, and also includes a friction plate 13 and a clutch interlocking lever mechanism 14. Reference numeral 15 denotes a primary deceleration driven wheel (sprocket), which is provided adjacent to the inner end of the drive housing 12.
5 is attached to the clutch 10 side via a clutch damper 16 and a connecting pin 17. Here, the primary deceleration driven wheel 15
is the center 18a in the width direction of the outer peripheral engaging portion 18
is the center 19a of the wheel disc 19 in the width direction.
In other words, the wheel disc 19 is disposed inward with respect to the outer circumferential engagement portion 18, and as a result, the clutch 10 as a whole is offset more than the conventional clutch 10 side. It is arranged on the inside by the same size as the width of the engine E, which will be described later.

On the other hand, a primary deceleration drive wheel 20 is integrally formed at the end b of the crankshaft B, and a silent chain 21 is stretched between the primary deceleration driven wheel 15 and the countershaft by the crankshaft B. C can be freely driven.

In particular, a balancer drive gear 22 is press-fitted into the end b of the crankshaft B, and the bearing wall 6 is disposed outside the balancer drive gear 22. In this case, both the balancer drive gear 22 and the bearing wall 6 are connected to the clutch 10.
radially outward (clutch 1 in engine E)
The space in front of the balancer drive gear 22 is effectively utilized, and the outer side of the balancer drive gear 22 is covered with a bearing wall 6 to suppress drive noise from escaping to the outside. Note that a through hole for installing the clutch 10 is formed in the bearing wall 6.

On the other hand, a balancer driven gear 24 driven by balancer drive gear 22 is shown in FIG. This balancer driven gear 24 is connected to the right bearing wall 6
and one end of the balancer shaft A supported between the left side bearing wall 6 (corresponding to the right side R of the engine E)
It is located in In this case, the balancer driven gear 24 includes an inner boss portion 25 that is press-fitted onto the outer circumference of the balancer shaft A, and an inner boss portion 25 that is press-fitted to the outer circumference of the balancer shaft A.
5, an outer circumferential gear 26 that can freely rotate relative to the inner circumferential boss portion 25, and a side with a pair of left and right fixing pins 27 that allow the above-mentioned relative rotation while preventing the outer circumferential gear portion 26 from coming off in the thrust direction with respect to the inner circumferential boss portion 25. ring plates 28, 28, inner boss portion 25 and outer gear portion 26
and a damper (spring) 29 provided between. Here, the balancer driven gear 24
is arranged inside the bearing wall 6, and in this case, its outer peripheral gear portion 26 is connected to the balancer drive gear 2.
The inner circumferential boss portion 25 is disposed in the same row as the outer circumferential gear portion 26 in the width direction.

Further, the balancer shaft A is formed of a hollow cylindrical body having an integrated balancer 30, and the balancer shaft A is connected to each left and right bearing wall 6 through bearing metals (bearing members) 31 and 32 forming a bearing part. , 6 are supported at both ends. In this case, each bearing metal 31, 32 has a circumferential groove 33 formed on its inner periphery, and each circumferential groove 33 of the balancer shaft A
Third oil passage holes 34 are formed in the radial direction (four locations) at locations corresponding to the respective locations.

In this way, one second oil passage hole 35 communicates with the circumferential groove 33 at the left end in FIG. Oil from an oil pan (not shown) introduced through a first oil passage (oil supply passage) (not shown) is guided by pumping, and from this second oil passage 35 to the circumferential groove 33.
The oil is guided into the fourth oil passage hole 36 of the balancer shaft A through the third oil passage hole 34 and the third oil passage hole 34 . Arrow Y indicates the refueling direction. In addition, 3
A closing cap 7 is provided at one end of the balancer shaft A. The oil thus derived is
Figure 2 right end side (corresponds to right side R of engine E)
is supplied to the bearing section.

The oil supply structure includes a fitting hole 38 formed at the end of the balancer shaft A, a screw hole 39 having a smaller diameter than the fitting hole 38 formed inside the fitting hole 38 in the axial direction, and a threaded hole 39 having a smaller diameter than the fitting hole 38. Further inward in the axial direction,
A fifth oil passage hole 40 is formed to communicate with the fourth oil passage hole 36, and the fifth oil passage hole 40 has a tapered shape to smoothly receive oil from the fourth oil passage hole 36. An oil guide surface 41 is formed. 42 is the pump drive shaft,
This is the shaft of the water pump 43, and the screw hole 39 is located inside the pump drive shaft 42 in the axial direction.
A screw shaft 44 on the small diameter side that is screwed into the fitting hole 38 somewhat loosely and a fitting shaft portion 45 that is tightly fitted into the fitting hole 38 are formed in a stepped shape. A sixth oil passage hole 46 is formed in the center of the screw shaft 44 and the fitting shaft part 45, and the oil from this sixth oil passage hole 46 is directed in the radial direction of the fitting shaft part 45. The oil is guided through the seventh oil passage hole 47 to a communication groove 48 on its outer periphery, and further, the oil from this communication groove 48 passes through the eighth oil passage hole 49 at four circumferential locations that penetrates the balancer shaft A in the radial direction. It is guided to the circumferential groove 33 of the bearing metal 32.

In this way, balancer shaft A and both bearing metal 3
Oil is supplied to the oil supply point formed between 1 and 32.

On the other hand, water pump (for engine cooling) 43
is fixed to the right outside of the balancer driven gear 24 across the bearing wall 6. This fixation is made removable using peripheral bolts (not shown). Since the water pump 43 is used for cooling water, there is little risk of cavitation even at high rotation speeds. A generator (not shown) is arranged in a protruding manner, and the balancer shaft A
This water pump 43 is located outside on the left side of Figure 2.
Since it is not possible to place the balancer shaft A, it is placed outside the right side of the balancer shaft A.

This water pump 43 has an inner casing 5
0 and an outer casing 52 disposed on the outside via a gasket 51 are combined and removably attached to the bearing wall 6 side using a mounting tool (not shown).

Here, 53 is a pump impeller, which is screwed to the outer end threaded portion 62 of the pump drive shaft 42. This screw tightening and the screw tightening of the pump drive shaft 42 itself to the balancer shaft A are set so that they do not loosen as the balancer shaft A rotates in a specific direction, but rather tighten easily. A seal seat 54 is fixed to the inner periphery of the pump impeller 53. An impeller-side seal 55 made of ceramic is fitted to the seal seat 54, while a retainer 56 is fitted on the pump drive shaft 42 side. A first shaft-side seal 57 is provided inside, and the first seal 57 is pressed against the impeller-side seal 55, which is the outside of the second shaft-side seal 59, by the elastic force of the sealing spring 58. , to prevent water from passing through the back (inside) space of the pump impeller 53 to the outside. Further, 60 is a gasket, 61 is a sealing member, and this sealing member 61 is connected to the outer end threaded portion 62 and the pump impeller 5.
Cooling water is prevented from flowing out from the water pump 43 through the gap between the water pumps 43 and 3.

Therefore, in the above configuration, oil is supplied to both of the bearing parts through the fourth oil passage hole 36 formed at the center of the balancer shaft A, so that the oil is supplied to the outside of the crankcase 2, especially the water pump 4.
There is no need for any piping on the third side, so not only is piping work unnecessary, but there is also less worry about oil leakage. In addition, crankcase 2
The exterior is simple, with no piping, which contributes to making it more compact.

In the above embodiment, the pump drive shaft 42 is removably screwed into the balancer shaft A, so that not only can maintenance of the water pump 43 be performed as necessary, but also the piping can be prevented from getting in the way during maintenance. Easy to work with. Also,
As in the embodiment, when the pump drive shaft 42 is deeply coupled with the bearing member 32 in a relationship that overlaps with the axial direction, a high degree of coupling is obtained, which stabilizes the pump drive and improves the balancing function of the balancer shaft A. Make it more stable. Not only that, but by creating such a deep bonding relationship,
The engine width has been made more compact. This compactness becomes even more remarkable by distributing the balancer driven gear 24 on the inside and the water pump 43 close to the outside with respect to the bearing wall 6. On the other hand, in this embodiment, a sixth oil passage hole 46 is formed in the center of the pump drive shaft 42 to stabilize the pump drive shaft 42 and also serve as an oil distribution function. It is something.

Further, in FIG. 2, the water pump 43 is installed as a water-cooled engine, but if this is an air-cooled engine, the water pump 43, including the removable pump drive shaft 42, may not be installed. In this case, a simple solution is to install a small closing cap (not shown) with a seal on the bearing wall 6 at a position corresponding to the inner casing 50 (Fig. 2) to prevent oil leakage. As a result, the engine itself can be standardized regardless of whether it is water-cooled or air-cooled. Furthermore, in the above embodiment,
The balancer driven gear 24 disposed at one end of the balancer shaft A and the water pump 43 are arranged inside the balancer driven gear 24 with the bearing wall 6 in the middle.
Also, since the water pump 43 is placed on the outside, the load balance on the balancer shaft A is better than when the balancer shaft A is extended and the balancer driven gear 24 and water pump 43 are provided at the outer end. , the original purpose of the balancing function is effectively exhibited, and the durability of the bearing and other rotational support members is improved.

Further, since the water pump 43 can use the bearing wall 6 as it is as the pump inner casing 50, the pump mounting structure becomes simple, and in this case, the bearing part can be cooled by the water pump 43. You can also do it.

Furthermore, since the bearing wall 6 is disposed outside the balancer driven gear 24, internal drive noise is difficult to dissipate to the outside, and for this reason, even if a side cover is provided outside the crankcase 2, the wall thickness is thin. This contributes to reducing the weight of the engine E.

(Effects of the invention) As explained above, according to this invention, lubricating oil from the crankcase is supplied from one bearing to the bearing on the water pump side through the oil hole in the balancer shaft. Therefore, it is important to lubricate between the balancer shaft and the bearing member, especially the bearing on the water pump side.
By passing it through the balancer shaft,
This eliminates the need for special external piping, eliminates the complexity of the structure of the oil supply system, and simplifies the structure.
The engine can be made more compact.

[Brief explanation of the drawing]

FIG. 1 is a sectional view showing an embodiment of this invention, and FIG. 2 is a sectional view showing a transmission system between a balancer shaft and a water pump. 2... Crank case, 6... Bearing wall, 31,
32... Bearing part (bearing member), 36... Oil hole, 42... Pump drive shaft, 43... Water pump, 46... Oil hole, A... Balancer shaft, B, 22... Drive mechanism , 24... Balancer driven gear, E... Engine, 30... Balancer,
53...Pump impeller.

Claims (1)

[Scope of utility model registration request] a bearing part set on mutually opposing bearing walls formed on both sides of the crankcase, a balancer shaft whose both ends are rotatably supported by the bearing parts, and a balancer shaft fixed to the outer periphery of the balancer shaft. a balancer; a water pump having a pump impeller set outside the crankcase and removably fixed to the pump drive shaft at the end of the balancer shaft; An oil passage extending and communicating with the bearing portion at both ends thereof, and an oil passage hole formed in a bearing wall supporting the opposite end of the balancer shaft in which the water pump is installed, and set in the bearing wall. an oil supply passage that communicates with the oil passage hole of the balancer shaft through the bearing section, a balancer driven gear fixed to the balancer shaft, and a balancer driven gear that transmits rotation from the engine to the balancer shaft. A mounting structure for a balancer and a water pump, characterized by comprising a drive mechanism that integrally rotates the pump impeller and the balancer.