JPH0619768Y2 - Lubricator for vertical axis engine - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION (Industrial field of application) The present invention is directed to a vertical axis type engine in which a crankshaft is arranged in a vertically extending posture, and in particular, a lubricating device used for such an engine is provided. Intended.

(Prior Art) In a vertical axis type engine, since a crank web and a crank pin rotate horizontally about a vertical axis, it is not possible to adopt a splash type lubrication method like a horizontal axis type engine.

Therefore, in the conventional vertical axis engine, an oil slinger is used as a lubricating device, as in Japanese Utility Model Laid-Open Nos. 58-14413 and 58-66105.

Another lubrication device is, for example, SAIKAI Sho 61-1755.
Trochoid pumps are used, such as No. 12 and No. 61-178013.

(Problems to be solved by the invention) However, in the conventional structure using the oil slinger, a slinger mounting shaft and a slinger drive device are required in addition to the crankshaft, which complicates the structure. Further, since a slinger device installation space and an oil scattering space are required, the entire crankcase becomes large. Further, since the lubrication is performed by splashing oil, it is difficult to supply the lubricating oil mainly to the portion requiring lubrication.

On the other hand, the structure using the trochoid pump has a disadvantage that the mounting space of the pump becomes large. In addition, the pump itself and the filter and the like attached to it are expensive. Furthermore, if a trochoid pump is installed in the middle of the crankshaft, the pump structure inevitably becomes large, and the pump capacity becomes unnecessarily large.

(Means for Solving the Problems) The present invention is directed to a large diameter portion 37 extending downward from the crank web 18 having an upward crank pin 19 on the output side.
And a bearing for supporting the upper end of the large diameter portion 37 of the crankshaft 1 and a bearing for supporting the small diameter portion 38, which has a small diameter portion 38 concentrically connected to the lower end of the large diameter portion 37 via a step 39. A bearing portion 3 including a hole 45 is provided in the crankcase 2, and the crankcase 2 between the bearing 5 and the bearing hole 45 is provided.
An oil sump 8 is formed between the crankshaft 1 and the crankshaft 1, and at the bottom of the oil sump 8, a through hole 33 having a circular cross section extending on the diameter of the upper end of the crankshaft small diameter portion 38 is movable at both ends thereof. A pair of cylindrical pins 11 to be fitted,
An annular shape fixed to the crankcase 2 with the center line R of the cylindrical inner circumferential surface 34 eccentric to the rotation center line O of the crankshaft 1 positioned outside the pin 11 and in contact with the step portion 39. Housing 12 and the crankshaft small-diameter portion 3
8 and the housing inner peripheral surface 34, the inlet 13 for connecting the wide portion in the radial direction of the pump chamber 35 and the oil sump 8, and the narrow portion in the radial direction of the pump chamber 35 are connected to the through hole 33. An oil pump 10 including an outlet 14 connected to an oil passage 17 at the center of the crankshaft extending upward from an intermediate portion of the oil passage 16 via an oil passage 16 having a diameter provided in the lower crankshaft small-diameter portion 38. And a radial oil passage 31 that extends radially outward from the oil passage 17 at the center of the crank shaft and reaches the inner surface of the bearing 5, and a crank pin 19 that extends obliquely upward from the oil passage 17 at the center of the crank shaft. And a tilted oil passage 28 reaching the surface of the vertical axis type engine lubrication device.

(Operation) According to the above configuration, the pin turns together with the crankshaft as the crankshaft rotates. The centrifugal force is generated in the pin by this swiveling action, so that the pin moves outward in the radial direction and keeps in contact with the inner peripheral surface of the housing, and the pump chamber is circumferentially separated by the pin. It is divided into parts. Further, since the housing is eccentric with respect to the crankshaft, the volume of each pump chamber portion changes as the pin swivels, and the volume increases when communicating with the inlet and decreases when communicating with the outlet. Become.

Therefore, the oil in the oil sump flows into the pump chamber portion having a large volume from the inlet, is compressed as the inlet is closed and the volume is reduced, and the pump chamber portion having the reduced volume is pressurized to the outlet. Is ejected.

(Embodiment) In FIG. 1 which is a schematic vertical sectional view, a crankshaft 1 is arranged in a vertical posture and is supported by a substantially cylindrical bearing portion 3 of a crankcase 2. A bearing 5 is interposed between the upper end of the bearing 3 and the crankshaft 1, and a seal 6 is interposed below the bearing hole 45 between the lower end of the bearing 3 and the crankshaft 1. . Upper half of crankshaft 1 (bearing 5
An oil sump 8 is formed around the lower side portion). The oil in the oil sump 8 is accumulated, for example, to a level L below the bearing 5 and above an oil pump 10 described later, so that the oil at the bottom of the oil sump 8 is supplied to the oil pump 10. Has become.

The oil pump 10 will be described later in detail, but basically,
A pair of cylindrical pins 1 extending in the radial direction of the crankshaft 1.
1 and an annular housing 12 located on the outer side in the radial direction with respect to the pin 11. The tip surface of the pin 11 facing the cylindrical inner peripheral surface 34 of the housing 12 is formed in a partially spherical shape. The housing 12 is fitted and fixed to the inner circumference of the crankcase bearing portion 3. The inlet 13 of the oil pump 10 is formed by cutting out a part of the upper end of the housing 12 and communicates with the bottom of the oil sump 8. The outlet 14 of the oil pump 10 is located at a position distant from the inlet 13 in the circumferential direction, and is adjacent to the inner periphery and the lower end of the housing 12. The outlet 14 is formed by a notch or a recess provided on the inner circumference of the bearing portion 3. An annular notch 46 for attaching the seal 6 is provided at the lower end of the bearing portion 3, and the bearing portion 3 is provided between the notch 46 for sealing and the housing 12 except for the outlet 14. The entire bearing hole 45 portion is fitted into the crankshaft 1 in a substantially close contact state.

An oil supply passage 15 communicating with the outlet 14 is provided inside the crankshaft 1, and the supply passage 15 has an oil passage 16 that penetrates the crankshaft 1 in the diametrical direction and is connected to the outlet 14, and an oil passage 16. Oil passage 1 extending upward from the center of the crankshaft 1
It is formed of 7 grades. The upper end of the oil passage 17 is open to the upper end surface of the crank web 18.

In the illustrated embodiment, only one crank web 18 is provided on the upper end of the crank shaft 1 projecting upward from the bearing 5 and extends in the horizontal direction. A crank pin 19 projects upward from the upper surface of one end of the crank web 18. The crank pin 19 has a connecting rod 2
The large ends of 0 are connected.

A guide plate 21 is fixed to the upper end of the crank pin 19. The guide plate 21 is substantially horizontal and extends from above the crank pin 19 to above the crank shaft 1.

In addition to the oil passages 16 and 17, the crankshaft 1, the crank web 18, and the crank pin 19 are provided with oil passages 28 and 29. The oil passage 28 extends obliquely inside the crankshaft 1 and the crank web 18 from the middle of the oil passage 17 and communicates with the center hole 30 of the crankpin 19. The oil passage 29 is provided in the crank pin 19, and extends from the inner peripheral surface of the crank pin 19 (from the center hole 30) to the outer peripheral surface farthest from the center line O of the crank shaft 1 of the crank pin 19.

Further, an oil passage 31 is connected to the oil passage 17 above the connection point with the oil passage 28. The oil passage 31 extends in the radial direction of the crankshaft 1 and opens toward the inner peripheral surface of the bearing 5.

The oil pump 10 is configured as shown in FIG. 2 (partial sectional view taken along the line II-II in FIG. 1). In FIG. 2, the crankshaft 1 is provided with a through hole 33 having a circular cross section in the diametrical direction, and the pair of pins 11 are respectively movable in the radial direction of the crankshaft 1 in the through hole 33. Is fitted in close contact with. Further, the annular housing 12 is cast into the crankcase 2 with the centerline R of at least the inner peripheral surface 34 (both the inner peripheral surface and the outer peripheral surface in the illustrated embodiment) being slightly eccentric with respect to the centerline O of the crankshaft 1. It is fixed by such means. Therefore, in the pump chamber 35 formed between the inner peripheral surface 34 and the outer peripheral surface of the crankshaft 1, a portion having a wide radial direction and a portion having a narrow radial direction are formed. The inlet 13 has a pump chamber 35 at a wide radial portion.
The outlet 14 is connected to the pump chamber 35 at a portion having a narrow radial width.

Further, in FIG. 1, the portion 37 of the crankshaft 1 in the oil sump 8 has a larger diameter than the lower portion 38, and a step 39 is formed between the portions 37, 38. The through hole 33 is formed at the upper end of the small diameter portion 38, and the annular end surface of the step portion 39 is seated on the upper end of the housing 12 in a relatively rotatable state over the entire circumference except the inlet 13.

According to the above configuration, the pin 11 pivots together with the crankshaft 1 as the crankshaft 1 rotates in the direction of arrow A. A centrifugal force is generated in the pin 11 by this turning operation, so that the pin 11 moves radially outward and moves toward the housing inner peripheral surface 34.
With the pin 11 as a boundary, the pump chamber 35 is divided into two pump chamber portions 40 (FIG. 2) in the circumferential direction. The inlet 13 and the outlet 14 are opened or closed in the pump chamber portion 40 by the pin 11 as the crankshaft 1 rotates. Further, since the inner peripheral surface 34 of the housing 12 is eccentric with respect to the crankshaft 1, the volume of each pump chamber portion 40 changes as the pin 11 turns, and the volume increases in a state of communicating with the inlet 13. , Exit 14
The volume becomes smaller in the state of communicating with.

Therefore, the oil in the oil sump 8 flows into the pump chamber portion 40 having a large volume from the inlet 13, is compressed as the inlet 13 is closed and the volume is reduced, and is added from the pump chamber portion 40 having the reduced volume. It is discharged to the outlet 14 under pressure.

The oil discharged to the outlet 14 reaches the center hole 30 through the oil passages 16, 17, and 28, is further pressurized by centrifugal force, and is fitted into the crank pin 19 and the connecting rod 20 from the center hole 30 through the oil passage 29. It flows to the joint (bearing surface).
A part of the oil is further pressurized from the oil passage 17 through the oil passage 31 by centrifugal force and supplied to the inner circumference of the bearing 5.

(Effect of the Invention) As described above, according to the present invention, the oil pump 10 is arranged between the crankshaft 1 and the crankcase bearing portion 3 so that the oil pump 10 is driven by the crankshaft 1. It is possible to simplify and reduce the weight. Needless to say, a dedicated drive shaft and a power transmission mechanism for driving the oil pump 10 are unnecessary, and the structure can be simplified in this respect as well.

Further, the oil passage structure can be simplified, and particularly by providing the supply passage 15 inside the crankshaft 1, the oil passage structure can be remarkably simplified. Further, also in the oil pump 10, the oil pump 10 can be configured by incorporating the pin 11 into the crankshaft 1 and disposing the annular housing 12 on the outer side thereof, so that the structure can be remarkably simplified.

In the present invention, since the through hole 33 has a circular cross section and the pin 11 has a columnar shape, not only the precision machining of the through hole 33 and the pin 11 is very easy but also the press fitting or the bolt is required for the assembling. Since there is no tightening step and loose fitting is all that is required, the number of assembly steps is reduced and the number of parts is small, which allows the oil pump 10 to be assembled inexpensively. Further, since the oil passage 16 is provided below the through hole 33, the connection with the outlet 14 is facilitated (a separate pipe is not required), and the oil passage 1
The vicinity of the lower end portion of the oil passage 17 centered on the crankshaft connected to the intermediate portion of 6 communicates with the space between the pins 11 and 11, and the pins 11 and 11 are connected to the space between the pins 11 and 11. Due to the pressure and the centrifugal force, the inner peripheral surface 34 of the housing is securely inscribed and rotates together with the crankshaft 1, so that the pump efficiency is improved.

(Another Embodiment) A compression coil spring may be arranged between the pair of pins 11.

In the structure of FIG. 1, the inlet 13 is formed in the housing 12, but instead of this structure, the inlet 13 can be formed in the outer periphery of the lower end of the large diameter portion 37 of the crankshaft 1 as shown in FIG. .

The inlet 13 of the embodiment shown in FIG. 3 is shown in FIG. 4 (IV-IV sectional partial view of FIG. 3).

In FIG. 4, the inlet 13 is provided on the outer periphery of the lower end of the large-diameter portion 37 of the crankshaft 1 in the shape of an arc near the pin 11 and on the rotation direction side of the pin 11, and as the crankshaft 1 rotates,
The pump chamber 35 has a wide radial portion.
It is formed so as to be opened and connected to the pump chamber at the upper end surface of the housing 12 at a portion having a narrow radial width.

Since the oil compression start time in the pump chamber 35 and the oil intake period from the inlet 13 correspond to the closing time of the inlet 13, the opening period of the inlet 13, etc., these closing time, closing period, etc. are set appropriately. Therefore, the position of the inlet 13 and the dimension in the circumferential direction can be variously changed. In other words, the optimum pump characteristics can be set only by appropriately setting the position and the circumferential dimension of the inlet 13.

[Brief description of drawings]

FIG. 1 is a schematic vertical sectional view of the embodiment, and FIG. 2 is II- of FIG.
II sectional partial view, FIG. 3 is a vertical sectional schematic view of another embodiment, and FIG. 4 is a IV-IV sectional partial view of FIG. DESCRIPTION OF SYMBOLS 1 ... Crank shaft, 2 ... Crank case, 3 ... Bearing part, 8 ... Oil sump, 10 ... Oil pump, 11 ... Pin, 12 ... Housing, 13 ... Inlet, 14 ... Outlet, 15 ... Oil supply path, 2
0 ... connecting rod, 33 ... through hole, 34 ... housing inner peripheral surface, 35 ... pump chamber, R ... housing inner peripheral surface center line, O ... crankshaft rotation center line

Continuation of front page (72) Creator Toshihiko Nishikawa 1-1 Kawasaki-cho, Akashi-shi, Hyogo Kawasaki Heavy Industries Co., Ltd. Akashi factory (56) References (JP, B1) Jitsuko Sho 52-32968 (JP, Y2)

Claims (1)

[Scope of utility model registration request] 1. A large-diameter portion 3 extending downward from an output side from a crank web 18 having an upward crank pin 19 on its upper surface.
7 and a bearing 5 for supporting the upper end of the large-diameter portion 37 of the crankshaft 1 having a small-diameter portion 38 concentrically continuous to the lower ends of the large-diameter portion 37 and the small-diameter portion 38. The bearing portion 3 including the bearing hole 45 is attached to the crankcase 2
And an oil sump 8 is formed between the crankcase 2 and the crankshaft 1 between the bearing 5 and the bearing hole 45, and the crankshaft small diameter portion 38 is formed at the bottom of the oil sump 8.
A pair of cylindrical pins 11 movably fitted at both ends to a through hole 33 having a circular cross section extending on the diameter of the upper end of the
The upper surface of the pin 11 is in contact with the step portion 39 outside the pin 11, and the center line R of the cylindrical inner peripheral surface 34 is eccentric to the rotation center line O of the crankshaft 1 and fixed to the crankcase 2. Annular housing 12, the pump chamber 3 between the crankshaft small diameter portion 38 and the housing inner peripheral surface 34.
The inlet 13 connecting the wide radial portion of 5 and the oil sump 8 and the narrow radial portion of the pump chamber 35 are provided in the crankshaft small diameter portion 38 below the through hole 33. And an outlet 14 connected to an oil passage 17 at the center of the crankshaft extending upward from the intermediate portion of the oil passage 16 via the oil passage 16 of The radial direction oil passage 31 extending outward in the direction to reach the inner surface of the bearing 5, and the crank pin 1 extending obliquely upward from the oil passage 17 at the center of the crankshaft.
9. A vertical axis engine lubrication device, characterized in that an inclined oil passage 28 reaching the surface of 9 is provided.