WO1998021062A1 - Structure de support vibro-isolante pour moteur a combustion interne a vilebrequin vertical - Google Patents
Structure de support vibro-isolante pour moteur a combustion interne a vilebrequin vertical Download PDFInfo
- Publication number
- WO1998021062A1 WO1998021062A1 PCT/JP1997/004090 JP9704090W WO9821062A1 WO 1998021062 A1 WO1998021062 A1 WO 1998021062A1 JP 9704090 W JP9704090 W JP 9704090W WO 9821062 A1 WO9821062 A1 WO 9821062A1
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- WIPO (PCT)
- Prior art keywords
- vibration
- internal combustion
- combustion engine
- power transmission
- vibration isolating
- Prior art date
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
- F16F15/04—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means
- F16F15/08—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means with rubber springs ; with springs made of rubber and metal
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K5/00—Arrangement or mounting of internal-combustion or jet-propulsion units
- B60K5/04—Arrangement or mounting of internal-combustion or jet-propulsion units with the engine main axis, e.g. crankshaft axis, transversely to the longitudinal centre line of the vehicle
- B60K5/06—Arrangement or mounting of internal-combustion or jet-propulsion units with the engine main axis, e.g. crankshaft axis, transversely to the longitudinal centre line of the vehicle with the engine main axis substantially vertical
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K5/00—Arrangement or mounting of internal-combustion or jet-propulsion units
- B60K5/12—Arrangement of engine supports
- B60K5/1208—Resilient supports
- B60K5/1216—Resilient supports characterised by the location of the supports relative to the motor or to each other
Definitions
- the present invention relates to an anti-vibration support structure for a vertical crankshaft internal combustion engine, which is applied to an anti-vibration support structure for an internal combustion engine with respect to a frame in, for example, a lawn tractor.
- internal combustion engines are generally of the horizontal crankshaft type (vertical cylinder type).
- a horizontal crankshaft is used in a mouth retractor having a disc mower M on the body abdomen.
- a horizontal crankshaft is used from the horizontal output shaft (power take-off shaft) 1 of a shaft internal combustion engine (hereinafter referred to as engine HE).
- engine HE shaft internal combustion engine
- a universal joint 4 is interposed between the vertical drive shaft 3 of the disc mower and a bevel gear mechanism. Or was interposed.
- an engine HE having a power transmission mechanism in which an endless belt for power transmission such as a belt or a chain is wound around an output shaft, that is, as shown in FIG. 2 or FIG.
- the belt tension F1 is a force uniformly applied in one direction (in FIGS. 2 and 3, the tension F1 is applied horizontally).
- the rotation torque F2 is Occurs when the engine HE is operated (particularly at startup), and this is the main engine starting force.
- the vibrating force mainly generated by the rotational torque F2 is large in the vertical direction. Therefore, as shown in FIG. 2 or 3, the upper surface of the frame B as the support of the engine HE is An anti-vibration support structure that mounts the internal combustion engine was adopted by interposing an anti-vibration member A between the engine and the bottom of the internal combustion engine.
- the vibration isolating member A having elasticity in the vertical and horizontal directions, It is better to set the spring constant to a small value in order to absorb the vertical vibrating force due to the rotational torque F2. That is, the fluctuation amount (flexibility) of the elastic body such as the vibration isolating rubber provided in the vibration isolating member is increased to absorb the vibration.
- a power transmission mechanism from a horizontal crankshaft type internal combustion engine to a vertical drive shaft requires a complex structure such as a universal joint or a bevel gear. If the transmission to the vertical drive shaft is performed from the output shaft of the vertical crankshaft type internal combustion engine, the power is transmitted from the vertical internal combustion engine output shaft to the vertical drive shaft.
- a power transmission mechanism with a simple structure using an endless belt for power transmission such as a belt or chain is sufficient.
- a vertical crankshaft type internal combustion engine that is, an output shaft 1 of the engine VE is attached.
- the belt 2 is wrapped around the drive pulley 3a attached to the drive shaft 3 of the disc mower M from the output pulley 1a), so that cost reduction can be realized and maintenance is also facilitated.
- the engine VE when a vertical crankshaft internal combustion engine (engine VE) is used, the engine VE is directly attached to the frame B as a support, as shown in Fig. 5 below. Vibrates in the horizontal rotation direction together with the internal combustion engine. If the frame B is, for example, a part of the vehicle body of the lawn tractor in FIG. 4, the vibration of the vehicle body increases with the vibration of the engine VE. Therefore, if the internal combustion engine is supported by the frame via the vibration isolating member, the frame can be damped, and depending on the position of the vibration isolating member, an excessive force is applied to the belt or chain. Can be avoided.
- the vibrating force generated by the rotational torque is also caused by the belt as an endless belt for power transmission. (Hereafter, it can be replaced with a chain.) Since the tension is generated in the horizontal direction, the required panel constant in the horizontal direction of the vibration isolator is inconsistent. In particular, where the directions of both forces coincide, for example, in the vibration isolator, the panel constant in the direction parallel to the directions of both forces is reduced (ie, the amount of flexure of the elastic body of the vibration isolator is increased).
- the vibrating force due to the rotational torque is absorbed and the vibration is reduced, but on the other hand, the displacement of the engine due to the belt tension increases, and the belt slips and undulates, thereby reducing the durability of the belt.
- the spring constant in this direction is set large (that is, the radius of the elastic body of the vibration isolating member is made small)
- the displacement of the internal combustion engine due to the pulling action of the belt is reduced, and the durability of the belt is reduced. Although it increases, it cannot absorb the vibrating force and the vibration increases.
- the vibration isolating support structure of the vertical crankshaft type internal combustion engine there are difficult problems in the structure and mounting position of the vibration isolating member.
- the rotation torque is generated by the rotation of the crankshaft or output shaft.Because the weight is not uniform throughout the internal combustion engine, the vibration is actually generated in the rotational direction around the center of gravity of the internal combustion engine. Forces may occur. This point must be taken into account when arranging the vibration isolating members.
- the vibrating force in the direction of rotational torque is considerably large at startup.
- the panel constant of the vibration isolating member is reduced and the directions are matched, the flexibility of the elastic body is increased, so that the deflection may exceed the limit.
- the present invention provides a vibration isolating support structure for a vertical crankshaft internal combustion engine as described below in order to solve the above problems.
- a vertical crank An endless belt for power transmission is wound around the output shaft of the shaft type internal combustion engine, and the internal combustion engine is supported on the support of the internal combustion engine through a plurality of vibration isolating members.
- a support for the internal combustion engine is provided with a portion for penetrating a vibration isolating member, and a space between the internal combustion engine and the vibration isolating member is provided. Remove.
- the vibration isolating member is formed by changing the direction of the tension of the endless belt for power transmission and the torque generated by the rotation of the output shaft. Is disposed at a position substantially orthogonal to the direction of Fourth, in the vibration isolating support structure of the vertical crankshaft type internal combustion engine, at least one vibration isolating member is disposed between the endless belts for power transmission or between the extension lines of the endless belt for power transmission. .
- At least one vibration isolating member includes an output shaft and extends in a tension direction of the endless belt for power transmission. Arrange on a parallel plane.
- the direction of the tension of the endless belt for power transmission shall be the resultant direction of the tension of the endless bands for power transmission.
- a vertical crank that winds an endless belt for power transmission from an output shaft of a vertical crankshaft type internal combustion engine, and supports the internal combustion engine in a vibration-isolated manner on a support of the internal combustion engine via a plurality of vibration isolation members.
- the anti-vibration members are arranged symmetrically via a plane parallel to the direction of the tension of the endless belt for power transmission and the output shaft and including the center of gravity.
- a vertical crank which winds an endless belt for power transmission from an output shaft of a vertical crankshaft type internal combustion engine and supports the internal combustion engine in a vibration-isolated manner on a support of the internal combustion engine via a plurality of vibration isolating members.
- an anti-vibration support structure for an axial internal combustion engine at least one of the anti-vibration members is disposed on a plane parallel to the tension direction of the endless belt for power transmission and the output shaft and including the center of gravity.
- the endless belt for power transmission is provided on the output shaft.
- the direction of the tension of the endless belt for power transmission is the resultant direction of the tension of the endless belts for power transmission.
- one of the directions is such that the larger the deflection, the more the direction becomes.
- at least one set of anti-vibration members is disposed so that the directions thereof are opposite to each other.
- FIG. 1 is a side view of a lawn tractor having a horizontal crankshaft type internal combustion engine.
- FIG. 2 is a front view showing the direction of force generated in a vibration isolating support structure of a horizontal crankshaft type internal combustion engine having an endless belt (belt) type power transmission mechanism, wherein the crankshaft and the output shaft are the same.
- FIG. 2 is a front view showing the direction of force generated in a vibration isolating support structure of a horizontal crankshaft type internal combustion engine having an endless belt (belt) type power transmission mechanism, wherein the crankshaft and the output shaft are the same.
- FIG. 3 is also a diagram when the crankshaft and the output shaft are different.
- FIG. 4 is a side view of a lawn tractor equipped with a vertical crankshaft internal combustion engine (engine VE).
- engine VE vertical crankshaft internal combustion engine
- FIG. 5 is a side view showing a structure for directly attaching the engine VE to the frame B.
- Fig. 6 is a side view showing the anti-vibration support of the engine VE with respect to the frame B via the anti-vibration member A, in a case where the anti-vibration member A is installed below the engine VE in the top-mounted type.
- FIG. 5 is a side view showing a structure for directly attaching the engine VE to the frame B.
- Fig. 6 is a side view showing the anti-vibration support of the engine VE with respect to the frame B via the anti-vibration member A, in a case where the anti-vibration member A is installed below the engine VE in the top-mounted type.
- FIG. 7 is also a view showing a case where the vibration isolating member A is arranged above the engine VE in the same manner as the top mounting type.
- FIG. 8 is also a view showing a case where the vibration isolating member A is arranged on the side of the engine VE in the same manner as the upper mounting type.
- FIG. 9 is a view showing a case where the vibration isolating member A is also arranged below the engine VE in the top-mounted type and the height of the bottom of the engine VE is uniform.
- FIG. 10 is also a view showing a case where the vibration isolating member A is disposed above the engine VE in a lower installation type.
- FIG. 11 is also a view showing a case where the vibration isolating member A is arranged on the side of the engine VE similarly in the lower installation type.
- FIG. 12 is also a diagram showing a case where the vibration isolating member A is arranged below the engine VE in the top installation type and the number of the vibration isolating members A is large.
- FIG. 13 is a view showing a case where the number of vibration isolating members A is further increased.
- FIG. 14 is a side view of a structure in which an anti-vibration member 4 is interposed between the frame B and the engine VE to support the anti-vibration when the output shaft 1 projects below the frame B.
- FIG. 15 is a side view of the structure for supporting the vibration isolator by removing the intervening space of the vibration isolator A between the frame B and the engine VE.
- FIG. 16 is a side view of the vibration isolating member A.
- FIG. 17 is also a front (plane) cross-sectional view.
- FIG. 18 shows the belt 2 applied to the position where the anti-vibration member A1 is provided when the center of gravity of the engine matches the output shaft (the direction of the vibrating force and the direction of the rotational torque F2 match).
- FIG. 4 is a plan view (bottom view) showing the directions of tension F 1 and rotation torque F 2 due to the rotation.
- FIG. 19 is a plan view (bottom view) of the engine VE showing an embodiment in which the vibration isolating member A1 is disposed at a position where the tension F1 and the rotational torque F2 are substantially orthogonal to each other.
- FIG. 20 is a diagram showing another embodiment.
- FIG. 21 is a view showing an embodiment in a case where the winding direction of the belt 2 is similarly changed by the tension pulley 13.
- Fig. 22 is a plan view (bottom view) of the engine VE when the vibration isolating member A1 is disposed at a position where the tension F1 and the rotation torque F2 are substantially orthogonal to each other.
- ⁇ It is a diagram when it is installed between two.
- FIG. 23 is a view showing a case where the vibration isolating member A 1 is similarly arranged between the belt extension lines 2 ′ and 2 ′.
- Fig. 24 is also a diagram of the case where the vibration isolating member A1 is disposed between the belts 2 and 2. You.
- FIG. 25 shows a case where the vibration isolating member A 1 is similarly disposed between the belts 2.
- FIG. 26 shows a case where the vibration isolating member A 1 is similarly disposed between the belts 2 and 2.
- FIG. 27 is a view showing a case where the vibration isolating member A 1 is similarly disposed between the belt extension lines 2 ′ and 2 ′.
- FIG. 28 is a plan view (bottom view) of the engine VE when the vibration isolating member A 2 is disposed on a plane S including the output shaft 1 and parallel to the direction of the tension F 1.
- FIG. 29 is a diagram showing another embodiment in the same manner.
- FIG. 30 is a view showing another embodiment in the same manner.
- FIG. 31 is a view showing another embodiment in the same manner.
- FIG. 32 is a view showing another embodiment in the same manner.
- FIG. 33 is a view showing another embodiment in the same manner.
- FIG. 34 is a diagram showing the direction of the resultant force F1c of the tensions F1a and F1b when a plurality of belts 2a and 2b are wound around the output burley 1a.
- FIG. 35 is a plan view (bottom view) of the engine VE in which a plane S including the center of gravity G serving as the center of the vibrating force F and a plane S parallel to the direction of the output shaft 1 and the tension F1 is set.
- FIG. 36 is a plan view (bottom view) of the engine VE showing a state in which the vibration isolating members A are arranged symmetrically via the plane S.
- FIG. 37 is a plan (bottom) view of the engine VE in which the vibration isolating member A3 is disposed on the plane S.
- FIG. 38 is a diagram showing another embodiment in the same manner.
- FIG. 39 is a diagram showing another embodiment in the same manner.
- FIG. 40 is a view showing another embodiment in the same manner.
- FIG. 41 is a plan view (bottom view) of the engine VE showing an arrangement position of the vibration isolating member A (A 2) including a plan sectional view of the vibration isolating member A (A 2).
- FIG. 42 is a side view of the engine VE showing an arrangement position of the vibration isolating member A (A 2).
- FIG. 43 is a plan view (bottom view) of the engine VE showing an embodiment of the arrangement positions of the three vibration isolating members A (A 2).
- FIG. 44 is a plan view (bottom view) of the engine VE showing an embodiment where four vibration isolating members A (A 2) are provided.
- FIG. 45 is a plan view (bottom view) of the engine VE showing an example of an arrangement position of the vibration damping member A having a characteristic of limiting the amount of deflection in one direction in the axial direction.
- FIG. 46 is a diagram showing the characteristic of the spring constant with respect to the amount of deflection of the vibration isolating member A in the direction of arrow N in FIG. 45.
- FIG. 47 is a plan view (bottom view) of the engine VE showing a specific structure of the vibration isolating member A having the characteristic of limiting the amount of radius in one direction in the axial direction and its mounting structure.
- FIG. 48 is also a view taken in the direction of the arrow X in FIG. 47.
- FIG. 49 is a sectional view taken along the line YY in FIG. BEST MODE FOR CARRYING OUT THE INVENTION
- a lawn tractor as shown in FIG. 4 is used. is there.
- a disc mower M is suspended from the abdomen of the lawn tractor, and projects vertically downward from the engine VE installed on the bonnet of the launch tractor with respect to the drive pulley 3a attached to the vertical drive shaft 3.
- Belt 2 is wound horizontally from output pulley ia attached to output shaft 1.
- the transmission mechanism is simplified as compared with the case where power is transmitted from the horizontal crankshaft type engine HE to the drive shaft 3 in FIG.
- the belt 2 may be replaced with the chain 2, in which case the output pulley 1a is replaced with the output sprocket 1a, and the drive pulley 3a is replaced with the drive sprocket 3a.
- the engine VE was directly attached to a frame B which is a part of the mouth retractor body.
- a tension F1 of the belt 2 and a rotation torque F2 accompanying rotation of the crankshaft CS are applied to the output shaft 1 protruding vertically downward, as in the case of the horizontal crankshaft engine HE.
- the tension F 1 is the force acting in the horizontal direction
- the rotational torque F 2 Is also horizontal. Accordingly, with the structure shown in FIG. 5, the frame B directly attached to the engine VE vibrates largely in the horizontal direction, and as a result, the horizontal vibration of the lawn tractor body increases.
- FIGS. 6 to 13 each embodiment shown in FIGS. 6 to 13 will be described.
- Each of the embodiments shown in FIGS. 6 to 9 has a structure in which a vibration isolating member A is disposed on a frame B, and a bracket with an engine VE or an engine VE is mounted thereon. ).
- Fig. 6 shows that the vibration isolating member A is interposed between the bottom of the engine VE and the upper surface of the frame B, and the vibration isolating member A is arranged below the engine VE.
- Fig. 7 shows a part of the mounting bracket 5 attached to the upper end of the engine VE mounted on the vibration isolating member A provided on the frame B.
- the vibration isolating member A is located above the engine VE.
- Fig. 8 shows a part of the mounting bracket 6 attached to the side of the engine VE installed on the vibration isolating member A arranged on the frame B. This is a type in which member A is arranged on the side of engine VE.
- FIG. 9 shows the same type as that of FIG. 6, in which the bottom height of the engine VE is not constant, so that the vibration isolating members A having different vertical lengths are used together.
- FIG. 10 is the same as FIG. 7 in that the anti-vibration member A is disposed above the engine VE
- FIG. 8 is the same as that shown in Fig. 8, but in each case, the type of mounting the engine VE or the bracket with the engine VE on the lower end of the vibration isolating member A suspended below frame B (lower In the case of Fig. 10, the upper end of the engine VE is installed at the lower end of the vibration isolating member A suspended from the frame B, and in the case of Fig. 11, the upper end of the frame B is installed. Attach the mounting bracket 7 attached to the side of the engine VE to the lower end of the vertically mounted anti-vibration member A.
- the anti-vibration support structure shown in FIGS. 12 and 13 is the same as that shown in FIG. 6 (upper mounting type where the anti-vibration member A is arranged below the engine VE). This type has many vibration members A.
- Fig. 6 (Fig. 9, Fig. 12 and Fig. 12)
- the frame B is located below the anti-vibration member A, the force with the engine VE installed above, and the lower part of the main body like the lawn tractor in Fig. 4.
- the output pulley 1a must protrude downward so as to pass through the frame B as the bottom of the main unit. No.
- the output shaft 1 becomes longer by the height H of the vibration isolating member A interposed between the upper surface of the frame B and the lower surface of the engine VE. If the output shaft 1 is long, the moment in the rotation direction will increase, and the deflection against the tension received from the belt 2 will also increase.
- the frame B is provided with holes for penetrating the vibration isolating member A, and Reduce the gap between the upper surface of B and the lower surface of engine VE.
- the output shaft 1 can be shortened by the height H of the vibration isolating member A.
- an engine-side mounting bracket 8 is interposed between the upper end of the anti-vibration member A and the bottom surface of the engine VE (the upper end of the anti-vibration member A is directly attached to the bottom surface of the engine VE).
- the lower end of the vibration isolating member A penetrating the frame B is mounted on a mounting bracket 9 attached to the frame B.
- the anti-vibration support of the engine VE to the frame B as described above in order to cope with the two horizontal forces, namely, the tension F 1 by the belt 2 and the rotational torque F 2, the anti-vibration in the horizontal direction is required.
- the location of the vibration member A is important.
- various embodiments regarding the arrangement position of the vibration isolation member A will be described.
- FIGS. 18, 19, 22, 28, 35 to 37, and 41 used to explain the arrangement position of the vibration isolating member A below
- the “planar (bottom) view” refers to the crankshaft (output shaft). Is a plan view when the engine VE is arranged upward from the top of the engine VE, and a bottom view when the engine VE is arranged so that the crankshaft (output shaft) faces downward as in the embodiment of FIG. It is.
- plane view when it is referred to as “plan view”, when applied to the embodiment in which the crankshaft (output shaft) is directed downward as shown in FIG. 4, this is replaced with “bottom view”. .
- the structure of the vibration isolation member A will be described first.
- Rough structure of anti-vibration member A As shown in Fig. 16 and Fig. 17, an elastic body 11 such as rubber is provided around a shaft core 10 which is a structure such as a female screw for screwing a bolt, as shown in Figs.
- An outer cylinder 12 is arranged around the periphery. Due to such a structure, the elastic body 11 of the vibration isolating member A has a large amount of fluctuation (low hardness) in the direction of the axis 10, and therefore, the panel constant K 2 (first (Fig.
- the structure is such that one direction is a direction with a large spring constant and a direction perpendicular to the direction is a direction with a small panel constant.
- a tension F1 to be dealt with in one direction with a large panel constant ⁇ 1 is applied, and a small spring constant ⁇ 2 is applied in a direction substantially perpendicular to it (0 ⁇ 90 °). If a vibration isolating member ⁇ is provided at a location where the rotational torque F 2 to be dealt with is applied, an effective vibration isolating effect can be obtained.
- FIGS. 19 to 27 show that at least one of the plurality of vibration isolating members A is disposed at a position where such a tension F 1 and a rotational torque F 2 are substantially orthogonal to each other (disposed at this position).
- the anti-vibration member to be installed is referred to as anti-vibration member A1.
- FIG. 19 shows a case where the vibration isolating member A1 is disposed between the belts 2 wound around the output pulley 1a.
- the vibration isolating member A1 is arranged on the side opposite to the winding side of the belt 2 via the output pulley 1a.
- the anti-vibration members A 1 and A 1 are disposed in the vicinity of the belts 2.2 where the direction of the tension F 1 and the direction of the rotational torque F 2 are substantially orthogonal.
- FIGS. 22 and 23 show the case where two anti-vibration members A except for the anti-vibration member A 1 are provided, FIG. 24 shows four of them, and FIG.
- Three vibration-absorbing members A other than the vibration-isolating member A 1 include the output shaft 1, and are connected to each other via a plane parallel to the tension F 1 of the belt 2.
- two anti-vibration members A are asymmetrically arranged via a plane including the output shaft 1 and parallel to the tension F1 of the belt 2. It is arranged in.
- At least one vibration isolating member (this is referred to as a vibration isolating member A2) is provided on a plane S including the output shaft 1 and parallel to the direction of the tension F1.
- the structure is Since the plane S includes the output shaft 1, the plane S is arranged in the diameter direction of a circle in a plan view around the output shaft 1, so that the rotational torque F 2 is applied in a direction orthogonal to the plane S. Therefore, the vibration isolating member A 2 disposed on the plane S has the same vibration isolating effect as the vibration isolating member A 1 because the tension F 1 and the rotational torque F 2 are applied in a direction substantially orthogonal to the vibration isolating member A 1. It is.
- the tension F1 is applied along the horizontal direction on the plane S, and the direction of the large panel constant of the vibration isolating member A2 is adjusted to this, and the rotation torque F2 is orthogonal to the plane S. Therefore, the direction in which the spring constant is small should be adjusted to this.
- this plane S may be arranged between the belts 2 as shown in FIGS. 29 and 32, or as shown in FIGS. 30, 31 and 33. As shown in the figure, it may be disposed on the side opposite to the winding side of the belt 2 via the output buries 1a.
- FIG. 28 shows an embodiment in which vibration isolating members A2 are provided on both sides. Further, the vibration isolating members A other than the vibration isolating member A 2 may be disposed at symmetric positions via the plane S as shown in FIGS. 29 to 31, or FIGS. As shown in Fig. 33, they may be arranged at asymmetric positions.
- the plane S is represented as a straight line in plan view.
- the positions of the vibration isolating member A1 or the vibration isolating member A2 shown in FIGS. 19 to 33 are determined when the single belt 2 is wound around the output pulley 11a. Is shown. However, there is a case where a plurality of pulleys are formed on the output pulley 1a and a plurality of belts are wound. In FIG. 34, the belt 2a and the belt 2b are wound around the output pulley 11a, and the winding directions are different from each other.
- the vibration isolating member A is provided at both a point substantially orthogonal to the tension F 1 a of the belt 2 a and the rotation torque F 2 and a point substantially orthogonal to the tension F 1 b of the belt 2 b and the rotation torque F 2. 1 or a plane including the output shaft 1 and both a plane parallel to the tension F1a of the belt 2a and a plane parallel to the tension F1b of the belt 2b.
- a 2 In order to obtain the effective vibration-damping effect with less vibration-absorbing member A1 or A2, the direction of the resultant force F1c of the tensions F1a and F1b should be changed to the belt 2a.
- the vibration isolating member A1 is disposed at a point substantially orthogonal to the resultant force Flc and the rotational torque F2, or on a plane parallel to the resultant force F1c including the output shaft 1. What is necessary is just to provide the vibration-proof member A2.
- FIGS. 18 to 34 The embodiment shown in FIGS. 18 to 34 described above is based on the premise that the direction of the vibrating force (referred to as F) of the engine VE and the direction of the rotational torque F2 match. is there.
- the vibrating force F of the engine VE is generated based on the rotational torque F2 of the crankshaft (output shaft), in fact, the direction of the vibratory force F does not necessarily correspond to the output shaft and the crankshaft. It does not coincide with the direction of the rotating torque F2 with respect to the center. This is because the weight may not be uniform throughout the engine VE.
- FIG. 35 a plane S 'that is parallel to the axis direction of the output shaft 1 and the direction of the tension F1 of the belt 2 and includes the center of gravity G (which is linear in plan view) is set. I do. As shown in the drawing, a vertical vibrating force F is applied to the plane S ′.
- FIGS. 36 to 40 An example of an arrangement position of the vibration isolating member A assuming the plane S ′ is shown in FIGS. 36 to 40.
- FIG. 36 shows a case where the vibration isolating members A are arranged symmetrically via the plane S ′, whereby at least the weight of the engine VE applied to each vibration isolating member A is evenly distributed. can do.
- one vibration isolating member A absorbs the tension F 1 with its large panel constant K 2 in the radial direction, and on the other hand, reduces the vibrating force F of the engine VE in the direction of its axis 10.
- At least one anti-vibration member A is disposed on this plane S ′ as shown in FIGS. 37 to 40 in order to absorb at a spring constant K1.
- the anti-vibration member A3 is shown in Fig. 37.)
- Fig. 37 shows two anti-vibration members A3 arranged on both sides of the plane S 'via the center of gravity G. Figs. In FIG.
- one anti-vibration member A 3 is disposed on the plane S ′, and the other anti-vibration members A are disposed on both sides thereof via the plane S ′.
- the vibration isolating members A arranged on both sides via the plane S ' Are disposed asymmetrically through the ridge.
- the arrangement of the vibration isolating member A (vibration isolating member A 3) shown in FIGS. 36 to 40 is based on the case where one belt 2 is wound around the output pulley 1 a.
- a plurality of belts 2 are also used.
- the anti-vibration member A (A3) may be provided with the plane S 'set assuming the resultant force of each tension. For example, when two belts 2a and 2b are wound around the output bur 1a, as shown in FIG. 34, the tensions F1a and F1b of each belt 2a and 2b are obtained.
- a plane S ′ is set, and the anti-vibration member A is disposed symmetrically via the plane S ′, Alternatively, at least one anti-vibration member A3 may be provided on the plane S '.
- FIGS. 41 to 44 an embodiment relating to the disposition position of the vibration isolating member A shown in FIGS. 41 to 44 will be described.
- the output shaft of the engine VE and the position of the center of gravity coincide with each other, and that the rotational torque F2 is a vibrating force.
- the direction in which the vibration isolating member A is arranged in a plan view is determined based on the structure in which the direction perpendicular to the direction is small and the direction perpendicular to the direction is small.
- the radial direction orthogonal to the axis 10 direction coincides with the tension F1 direction (that is, FIGS. 28 to 3).
- the arrangement is the same as that of the anti-vibration member A 2 on the plane S disclosed in Fig. 3.) While absorbing the vibrating force due to the rotational torque F 2 and making the resistance to the tension F 1 particularly strong, The displacement of the engine VE due to the tension action of the belt 2 can be effectively suppressed.
- the spring constant K2 increases as the radius L increases beyond a certain value, as shown in Fig. 46, so that the amount of deflection can be limited.
- the direction of the arrow N in each of the vibration isolating members A in FIG. Show this direction.
- the outer peripheral shape is tapered so that the panel constant K 2 increases when the amount of deflection L is large in only one direction in the axial direction.
- a shaft 10 is used.
- the outer cylinder 12 also has a tapered shape corresponding to it, and an elastic body 11 is interposed between the shaft core 10 and the outer cylinder 12.
- the elastic body 11 Due to such a structure, the elastic body 11 has a large allowable bending amount (small spring constant) from the shorter outer diameter to the longer outer diameter of the shaft core 10, but the elastic body 11 has the larger outer diameter from the longer outer diameter to the shorter one. As the bending increases, the panel constant K 2 increases, and the allowable amount of bending is limited. This direction
- the shaft core 10 is a female screw or the like, into which the port 13 is screwed.
- a frame-side mounting bracket 9 is attached to the frame B, and the end of the outer cylinder 12 of the vibration-proof member A is fixed to the frame-side mounting bracket 9. This is the position where the anti-vibration member A is to be attached in a plan view.
- anti-vibration members A e, A f, and A g The direction N in which the rotational torque F 2 around 1 a is applied and the direction in which the amount of deflection of the elastic body 11 is limited with respect to the vibration isolating members A e and A f are opposed to each other. It is arranged in the direction that it does.
- the belt is wound around the output pulley 1a so that the tension F1 of the belt 2 is not parallel to the direction 10.
- Belt 2 is shown as a dashed line 2 ′ in FIG.
- the anti-vibration member Ag is disposed at the position where the tension F1 and the rotation torque F2 are orthogonal to each other (the above-mentioned plane S). This corresponds to the illustrated anti-vibration member A 2.
- the anti-vibration support structure of the vertical crankshaft type internal combustion engine as described above has the following effects.
- the power transmission mechanism is endless for power transmission of belts, chains, etc.
- a belt for example, like a lawn tractor, a vertical drive shaft for mower drive provided on the abdomen of the vehicle is connected to an endless belt for power transmission such as a belt or chain from a vertical crank shaft. Transmission is possible, the transmission mechanism from the output shaft to the drive shaft is simplified, and maintenance is facilitated.
- the support for the internal combustion engine is provided with a vibration isolating member penetrating portion, Eliminate the space between the internal combustion engine and the vibration isolating member.
- the interposition of the vibration isolating member between the frame and the internal combustion engine is eliminated, and the length of the output shaft projecting below the frame can be shortened accordingly, and the amplitude can be suppressed.
- the vibration isolating member Due to its structure, the vibration isolating member has a small panel constant in one direction and a large spring constant in a direction perpendicular to the panel constant.
- an endless belt for power transmission such as a belt or a chain
- the tension of the endless belt for power transmission applied to the internal combustion engine and the rotation of the crankshaft.
- the rotating torque to be applied are all horizontal directions. Therefore, depending on the position, the direction of the tension and the direction of the rotational torque may be completely the same.
- the vibration isolating member can be more reliably arranged by being disposed between the endless belts for power transmission or between the extension lines of the endless belt for power transmission.
- the tension and the rotation torque are close to the position where the torque is orthogonal to each other, so that the vibration isolation can be improved, and the displacement effect of the internal combustion engine due to the tension of the endless belt for power transmission is reduced. Slip vibrations such as noise can be suppressed.
- a plane including the output shaft and parallel to the tension is subjected to a horizontal tension along the plane, and a rotational torque is applied orthogonally to the plane. Therefore, as described in the fifth aspect of the disclosure of the invention, by arranging at least one vibration isolating member on the plane, the direction in which the panel constant is large matches the direction in which tension is applied, and the spring constant is reduced. The smaller direction can be made to correspond to the direction in which the rotational torque is applied, and both can be absorbed by a single anti-vibration member, and an effective anti-vibration effect can be obtained with a small number of anti-vibration members. Suppresses the displacement of the endless belt for tension due to the pulling action, and avoids the slip and wave motion of the belt or chain as the endless belt for power transmission.
- the endless belt for power transmission wound around a plurality of output shafts by taking the sixth description in the disclosure of the invention, it is possible to prevent the endless belt for power transmission by coping with each tension direction of each endless belt for power transmission. Even if the vibration member is not provided, the tension direction of the plurality of endless belts for power transmission can be unified in the resultant force direction, and the resultant force direction and the rotational torque are substantially orthogonal to each other, or the output shaft. If at least one damping member is provided on a plane parallel to the resultant force direction, an effective damping effect and a displacement suppressing effect of the internal combustion engine can be obtained.
- the weight may not be evenly distributed, and the position of the output shaft (crankshaft) and the center of gravity may be shifted.
- the vibration isolating member is used. Are arranged in parallel with the direction of the tension of the endless belt for power transmission such as belt and tune and the output shaft, and symmetrically via a plane including the center of gravity, so that at least the internal Is made uniform in weight.
- At least one of the vibration damping members is arranged on a plane parallel to the tension direction of the endless belt for transmitting power and the output shaft and including the center of gravity.
- the tension of the endless belt for power transmission and the vibrating force of the internal combustion engine are applied to the vibration isolator in a direction substantially orthogonal to the direction of the spring constant.
- the tension direction of the plurality of endless belts for power transmission can be unified in the direction of the resultant force without providing a vibration isolating member, and a plane parallel to the direction of the resultant force and the output shaft and including the center of gravity can be formed.
- the vibration isolating member is moved in a direction in which the panel constant is small. Is arranged so as to match the direction of action of the vibrating force, the vibrating force of the internal combustion engine can be absorbed with a large spring constant. By arranging it in a position where the direction of action of the tension and the direction of action of the vibrating force do not match, an action with a large spring constant can be provided in the direction of the tension, and the internal combustion engine is pulled by the endless belt for power transmission. Can be suppressed. In this way, both forces can be handled by one vibration isolating member, and an effective vibration isolating effect can be obtained.
- the vibration isolating member may be damaged or its durability may be weakened, but as described in the eleventh embodiment described in the disclosure of the present invention, the direction of the action of the vibrating force on the vibration isolating member is considered.
- one of the directions has a characteristic that the spring constant in that direction increases as the bending increases, and in this direction, the bending when a large vibrating force is generated
- the amount of radius can be limited in both directions in the axial direction. Improved anti-vibration effect, It contributes to durability of the member.
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- Transportation (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- Vibration Prevention Devices (AREA)
- Arrangement Or Mounting Of Propulsion Units For Vehicles (AREA)
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US09/297,807 US6293880B1 (en) | 1996-11-11 | 1997-11-10 | Vibro-isolating supporting structure for vertical crankshaft internal combustion engine |
DE69729205T DE69729205T2 (de) | 1996-11-11 | 1997-11-10 | Schwingungsisolierende tragstruktur für brennkraftmaschinen mit vertikaler kurbelwelle |
EP97911505A EP0934843B1 (en) | 1996-11-11 | 1997-11-10 | Vibro-isolating supporting structure for vertical crankshaft internal combustion engine |
Applications Claiming Priority (6)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP8/299122 | 1996-11-11 | ||
JP8/299121 | 1996-11-11 | ||
JP8/299120 | 1996-11-11 | ||
JP29912196A JPH10138768A (ja) | 1996-11-11 | 1996-11-11 | 垂直クランク軸式内燃機関の防振支持構造 |
JP29912096A JPH10141438A (ja) | 1996-11-11 | 1996-11-11 | 垂直クランク軸式内燃機関の防振支持構造 |
JP29912296A JP3621212B2 (ja) | 1996-11-11 | 1996-11-11 | 垂直クランク軸式内燃機関の防振支持構造 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO1998021062A1 true WO1998021062A1 (fr) | 1998-05-22 |
Family
ID=27338276
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP1997/004090 WO1998021062A1 (fr) | 1996-11-11 | 1997-11-10 | Structure de support vibro-isolante pour moteur a combustion interne a vilebrequin vertical |
Country Status (4)
Country | Link |
---|---|
US (1) | US6293880B1 (ja) |
EP (1) | EP0934843B1 (ja) |
DE (1) | DE69729205T2 (ja) |
WO (1) | WO1998021062A1 (ja) |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US9797498B2 (en) | 2013-05-23 | 2017-10-24 | Litens Automotive Partnership | Isolator with double acting spring system with reduced noise |
US10041578B2 (en) | 2013-07-25 | 2018-08-07 | Litens Automotive Partnership | Spring assembly for isolator |
US10060502B2 (en) | 2012-10-12 | 2018-08-28 | Litens Automotive Partnership | Isolator for use with engine that is assisted or started by an MGU or a motor through an endless drive member |
US10125856B2 (en) | 2013-11-10 | 2018-11-13 | Litens Automotive Partnership | Isolator with dual springs |
US10267405B2 (en) | 2013-07-24 | 2019-04-23 | Litens Automotive Partnership | Isolator with improved damping structure |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE60309917T2 (de) * | 2002-10-14 | 2007-03-08 | Mtd Products Inc., Valley City | Schwingungsdämpfungsanordnung |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS61125824U (ja) * | 1985-01-29 | 1986-08-07 | ||
JPS61135720U (ja) * | 1985-02-14 | 1986-08-23 | ||
JPH06288436A (ja) * | 1993-03-31 | 1994-10-11 | Yanmar Agricult Equip Co Ltd | 移動農機 |
Family Cites Families (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3429533A (en) * | 1967-10-23 | 1969-02-25 | Briggs & Stratton Corp | Vibration absorbing mounting for single - cylinder vertical shaft engine |
US3841425A (en) * | 1973-10-26 | 1974-10-15 | Briggs & Stratton Corp | Controlled vibration absorbing mounting for engines |
US3951223A (en) * | 1974-08-20 | 1976-04-20 | Briggs & Stratton Corporation | Tractor vehicle structural arrangement that minimizes vibration |
FR2356532A1 (fr) * | 1976-06-30 | 1978-01-27 | Motobecane Ateliers | Fixation de moteur pour vehicules et notamment pour cyclomoteurs |
JPS61125824A (ja) | 1984-11-22 | 1986-06-13 | Hitachi Ltd | 射出圧縮成形金型 |
JPS61135720A (ja) | 1984-12-07 | 1986-06-23 | Toyota Motor Corp | 射出成形機の自動色替方法 |
JPH01238752A (ja) * | 1988-03-17 | 1989-09-22 | Yamaha Motor Co Ltd | 芝刈機のベルトテンション装置 |
JP3399138B2 (ja) * | 1995-02-24 | 2003-04-21 | 日産自動車株式会社 | 防振支持装置 |
-
1997
- 1997-11-10 US US09/297,807 patent/US6293880B1/en not_active Expired - Fee Related
- 1997-11-10 DE DE69729205T patent/DE69729205T2/de not_active Expired - Lifetime
- 1997-11-10 WO PCT/JP1997/004090 patent/WO1998021062A1/ja active IP Right Grant
- 1997-11-10 EP EP97911505A patent/EP0934843B1/en not_active Expired - Lifetime
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS61125824U (ja) * | 1985-01-29 | 1986-08-07 | ||
JPS61135720U (ja) * | 1985-02-14 | 1986-08-23 | ||
JPH06288436A (ja) * | 1993-03-31 | 1994-10-11 | Yanmar Agricult Equip Co Ltd | 移動農機 |
Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US10060502B2 (en) | 2012-10-12 | 2018-08-28 | Litens Automotive Partnership | Isolator for use with engine that is assisted or started by an MGU or a motor through an endless drive member |
US9797498B2 (en) | 2013-05-23 | 2017-10-24 | Litens Automotive Partnership | Isolator with double acting spring system with reduced noise |
US10690228B2 (en) | 2013-05-23 | 2020-06-23 | Litens Automotive Partnership | Isolator with double acting spring system with reduced noise |
US10267405B2 (en) | 2013-07-24 | 2019-04-23 | Litens Automotive Partnership | Isolator with improved damping structure |
US10041578B2 (en) | 2013-07-25 | 2018-08-07 | Litens Automotive Partnership | Spring assembly for isolator |
US10125856B2 (en) | 2013-11-10 | 2018-11-13 | Litens Automotive Partnership | Isolator with dual springs |
Also Published As
Publication number | Publication date |
---|---|
DE69729205D1 (de) | 2004-06-24 |
EP0934843A4 (en) | 2000-01-19 |
DE69729205T2 (de) | 2005-05-19 |
US6293880B1 (en) | 2001-09-25 |
EP0934843B1 (en) | 2004-05-19 |
EP0934843A1 (en) | 1999-08-11 |
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