JP5330707B2 - Vibration isolator for industrial machinery - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a vibration control system for an industrial machine requiring reduced power for a vibration control section and offering improved vibration control performance, power consumption, and working efficiency. <P>SOLUTION: A power reduction means 47 has flow passage selector valves 42, 42a, 42b, 42d, 42e, and an accumulator 46 provided for a flow passage 36 between a pumping section 37 and a cylinder liner 33, a machine body has a vibration detector 35 to detect the vibration of the machine body, and the flow passage selector valves 42, 42a, 42b, 42d, 42e and the vibration detector 35 are connected to the control section 39. The machine body also has a vibration detector 35, and the flow passage selector valve 42 and the vibration detector 35 are connected to the control section 39. <P>COPYRIGHT: (C)2009,JPO&amp;INPIT

Description

  The present invention includes an anti-vibration unit between an upper body and a lower body constituting the airframe, and the anti-vibration unit can supply and discharge an anti-vibration member connected to a flow path provided with a pressure feeding unit and a relief valve. A cylinder liner and a cylinder that is slidable inside the cylinder liner and has one end attached to the upper body or the lower body, and depending on the direction and amplitude of vibration propagating from the upper body or the lower body, By supplying and discharging a vibration isolating member in the cylinder liner and adjusting the amount of the vibration isolating member in the cylinder liner, the internal pressure of the cylinder liner is kept constant before and after the vibration load to prevent the upper body or the lower body. The present invention relates to a vibration isolator for an industrial machine that vibrates. More specifically, the vibration isolator includes power reducing means and also relates to improvement of the vibration isolating performance.

  In a conventional work vehicle such as a tractor, a vibration isolating rubber is provided between the fuselage and the cabin as a method for isolating a control unit having a cabin or the like from vibrations input to the vehicle body due to unevenness of the road surface during traveling. There is something with. Also, when the hydraulic pressure that balances the piston load of the hydraulic cylinder attached to the control section to be vibration-isolated is adjusted with the relief valve, and the traveling part integrated with the cylinder liner of the hydraulic cylinder is vibrated in the axial direction of the hydraulic cylinder There is also a technique for keeping the internal pressure of the hydraulic cylinder constant before and after the vibration is applied by operating the relief valve to dampen the control unit (for example, Patent Document 1 and Non-Patent Document 1).

JP 2006-27342 A Agricultural Machinery Society Kansai Branch Report No. 48 (June 1980)

However, in such a work vehicle of Patent Document 1, the vibration control rubber absorbs vibrations and the control part is vibration-proof. Therefore, the control part is provided for particularly moderate or higher vibrations received from the road surface during traveling. There was a problem that the image could not be adequately isolated. Therefore, when the anti-vibration technology as in Non-Patent Document 1 is used for a work vehicle, for example, hydraulic oil in the transmission case is supplied into the hydraulic cylinder by a hydraulic pump, and the internal pressure of the hydraulic cylinder is kept constant before and after the vibration is applied. The parts to be held and vibration-proofed are vibration-isolated, but in order to maintain the internal pressure of this hydraulic cylinder, it is necessary to keep the hydraulic pump driven at all times. there were.
In addition to the above-described problems, in such a hydraulic cylinder, the piston is slid by supplying and discharging hydraulic oil or the like in order to keep the internal pressure of the hydraulic cylinder constant before and after the vibration is applied. Since the cylinder liner and the cylinder liner have a large frictional force, there is a problem that the smooth sliding of the piston is hindered and the vibration isolation effect of the portion to be isolated by the hydraulic cylinder is reduced.
SUMMARY OF THE INVENTION Accordingly, an object of the present invention is to provide a vibration isolator for an industrial machine that improves the fuel efficiency and workability while reducing the power of the vibration isolator and improving the vibration isolation performance.

For this reason, the invention according to claim 1 includes an anti-vibration unit between an upper body and a lower body constituting the airframe, and the anti-vibration unit is connected to a flow path provided with a pressure feeding unit and a relief valve. A cylinder liner that is capable of supplying and discharging a vibration isolating member, and a cylinder that is slidable in the cylinder liner and has one end attached to the upper body or the lower body, the upper body or the lower body According to the direction and amplitude of the vibration propagating from the body, the internal pressure of the cylinder liner is adjusted by supplying and discharging the vibration isolating member in the cylinder liner and adjusting the amount of the vibration isolating member in the cylinder liner. Is maintained constant before and after the vibration load, and the vibration isolator of the industrial machine that isolates the upper body or the lower body, the anti-vibration unit has a driving force of the anti-vibration unit at low vibration below a set vibration light the overload To, characterized in that it comprises a power reducing means.

According to a second aspect of the present invention, in the vibration isolator for an industrial machine according to the first aspect, the power reducing means is provided in the flow path between the pressure feeding unit and the cylinder liner by the pressure feeding unit. A flow path switching valve that passes or blocks the vibration isolation member, and one accumulator, and the airframe includes a vibration detector that detects vibration of the airframe, the flow path switching valve, A vibration detector is connected to the control unit.

According to a third aspect of the present invention, in the vibration isolator for an industrial machine according to the second aspect , the power reducing means is provided in the cylinder liner with an elastic body attached to a piston head of the piston, The flow path between the cylinder liner and the cylinder liner includes the flow path switching valve, the body includes the vibration detector, and the flow path switching valve and the vibration detector are controlled by the control unit. It connects to a part.

  According to a fourth aspect of the present invention, in the vibration isolator for an industrial machine according to the first aspect, the cylinder includes a rotation mechanism that rotates the cylinder.

According to a fifth aspect of the present invention, in the vibration isolator for an industrial machine according to the fourth aspect , the rotating mechanism and the vibration detector are connected to the control unit.

According to a sixth aspect of the present invention, in the vibration isolator for an industrial machine according to the fourth aspect , the rotating mechanism is driven by a discharge flow rate of the vibration isolating member from a relief valve that adjusts an internal pressure of the cylinder liner. It is characterized by doing.

According to the first aspect of the present invention, the anti-vibration unit is provided between the upper body and the lower body constituting the airframe, and the anti-vibration unit is connected to the flow path provided with the pressure feeding unit and the relief valve. A cylinder liner that can supply and discharge members, and a cylinder that is slidable in the cylinder liner and that has one end attached to the upper body or lower body, and that transmits vibrations propagating from the upper body or lower body. Depending on the direction and amplitude, the damping member is fed into and discharged from the cylinder liner, and the amount of the damping member in the cylinder liner is adjusted, so that the internal pressure of the cylinder liner is kept constant before and after the vibration load, In the vibration isolator of the industrial machine that vibrates the upper body or the lower body, the vibration isolator includes a power reduction means that reduces the overload of the driving force of the vibration isolator at a low vibration below the set vibration . Hydraulic pressure due to overload While preventing damage to the pumping unit, such as flop, it is possible to improve the fuel consumption of the aircraft. Accordingly, it is possible to provide an industrial machine vibration isolator having improved fuel efficiency and workability.

According to the second aspect of the present invention, the power reducing means includes a flow path switching valve that passes or blocks the vibration isolating member by the pressure feeding section in the flow path between the pressure feeding section and the cylinder liner . In addition to accumulators, the fuselage is equipped with a vibration detector that detects the vibration of the fuselage, and the flow path switching valve and the vibration detector are connected to the control unit. In the case of anti-vibration when necessary, the anti-vibration part can be switched from the cylinder operation by the anti-vibration member from the pumping part to the cylinder operation by the accumulator air pressure to reduce the driving force of the pumping part. Can do. Therefore, it is possible to provide an industrial machine vibration isolator with improved fuel efficiency.

According to a third aspect of the present invention, the power reducing means is provided in the cylinder liner , wherein the elastic body is attached to the piston head of the piston , and the flow path switching valve is provided in the flow path between the pressure feeding portion and the cylinder liner. In addition, the airframe is provided with a vibration detector, and the flow path switching valve and the vibration detector are connected to the control unit. Therefore, when vibration applied to the airframe is small, the vibration isolator supplied by the pressure feeding unit is provided. Since the part that should be vibration-isolated is switched from the operation of the cylinder by the member to the operation of the cylinder by the expansion and contraction of the elastic body in the piston and the vibration of the anti-vibration member in the cylinder liner, the power of the pumping part is reduced. be able to. Therefore, it is possible to provide an industrial machine vibration isolator with improved fuel efficiency.

  According to the fourth aspect of the present invention, since the cylinder includes a rotation mechanism that rotates the cylinder, the frictional force between the piston and the cylinder liner is reduced by applying dynamic friction to the piston of the vibration isolating portion. By smoothly sliding, it is possible to improve the vibration reduction effect of the portion to be vibrated. Accordingly, it is possible to provide a vibration isolator for an industrial machine that improves the vibration isolating performance of the vibration isolator.

  According to the fifth aspect of the invention, since the rotation mechanism and the vibration detector are connected to the control unit, the rotation mechanism is driven only when the airframe receives a large vibration, and the power of the rotation mechanism is increased. In addition to reducing the friction of the sliding surface between the piston and the cylinder liner by applying dynamic friction to the cylinder, the durability of the sealing material can be improved. Accordingly, it is possible to provide a vibration isolator for an industrial machine that is reduced in cost and fuel efficiency.

  According to the invention described in claim 6, since the rotating mechanism is driven by the discharge flow rate of the vibration isolating member discharged from the relief valve, a separate device for controlling the rotating mechanism is not required, and the rotating mechanism has a simple configuration. Can be driven. Accordingly, it is possible to provide a vibration isolator for an industrial machine in which the vibration isolating performance of the vibration isolator is improved at a low cost.

Hereinafter, the best mode for carrying out the present invention will be described in detail with reference to the drawings.
FIG. 1 is a left side view of a wheeled tractor as a work vehicle showing an embodiment of an industrial machine having an upper body and a lower body of the present invention, and FIG. 2 is a plan view of the tractor.

  As an industrial machine of this example, a tractor 1 of a work vehicle includes a front wheel 3 and a rear wheel 4 before and after a body frame 2, and a bonnet 5 is formed above the front wheel 3. An engine 6 and a clutch housing 7 are disposed, and a transmission case 8 is disposed at the rear of the clutch housing 7, and power from the engine 6 is transmitted to the front wheels 3 and the rear wheels 4. A cabin 9 as an upper body 1A is provided on the body frame 2 continuously to the rear part of the bonnet 5 of the lower body 1B having such a configuration. In addition, the tractor 1 may be a lops specification in addition to the cabin specification as described above.

  Next, an operating pedal 10 such as a brake pedal or a clutch pedal, a steering handle 11, a seat 12 and the like are provided in the cabin 9 as a control unit. Further, on the left and right fenders (not shown) provided on both sides of the seat 12, for example, various operation levers such as a main transmission lever 14, a sub transmission lever, and a PTO transmission lever are projected. Further, a windshield 15, a rear glass 16, a door 17, a roof 18 and the like may be attached to the outer periphery of the cabin 9, respectively.

  The power of the engine 6 is transmitted to a PTO shaft (not shown) protruding forward and backward from the mission case 8, and driven by the universal joint at the rear end of the vehicle, the lift link 19 and the left and right lower links 20 by driving the PTO shaft. A working machine (not shown) mounted on the rear end of the vehicle is driven via a working machine mounting device 21 such as a three-point link type.

  Next, a specific configuration of the vibration isolator of the vibration isolator having the power reducing means according to the present invention will be described. FIG. 3 is a perspective view of a tractor including a vibration isolator as viewed from the front, FIG. 4 is a schematic diagram illustrating an installation position of the vibration isolator, and FIG. 5 is a side view of the vibration isolator showing an example of power reducing means in the vibration isolator. It is a schematic diagram.

  First, as shown in FIG. 3, a bonnet 5 or a mission case having an upper body 1A such as a cabin 9 having a steering section, a front wheel 3 and a rear wheel 4 and having an engine 6 mounted on the vehicle body frame 2 provided therein. 8 and the lower body 1B composed of 8 and the like, and on the vehicle body frame 2, an anti-vibration for preventing the upper body 1A from vibrations input to the vehicle body due to road surface unevenness during traveling. A vibration unit 31 is provided.

  For example, as shown in FIG. 4, the vibration isolator 31 is a cylinder s composed of a piston 32 and a cylinder liner 33. For example, the upper body 1A on the vehicle body frame 2 located at the upper end of the lower body 1B. One location is provided near the front center of the bottom portion, and one location on the left and right of the rear portion of the bottom of the upper body 1A and on the left and right of the rear portion of the body frame 2. In addition, the installation number and installation location of the vibration isolator 31 are not limited to the above.

  Further, the vibration isolator 31 will be described in detail with reference to an example below. FIG. 5 shows one of the cylinders s of the above-described vibration isolator 31. The upper end of the piston 32 with the piston head 32a facing downward is fixed to the bottom of the upper body 1A. In addition, a lower end portion of a cylinder liner 33 that allows the piston head 32a to be inserted from above is fixed on the vehicle body frame 2 of the lower body 1B.

  In addition, at an appropriate position of the upper body 1A or the lower body 1B (which may be both the upper body 1A and the lower body 1B), vibration that is vibrated by the airframe is detected. The vibration detector 35 is not limited in the type of detection method and sensor, such as a displacement sensor such as a current type and an acceleration sensor such as a piezoelectric element type.

  Further, a gap between the middle portion of the cylinder liner 33 (between the lower end of the cylinder liner 33 and the piston head 32a slidably inserted into the cylinder liner 33) and the inside of the transmission case 8 is prevented. A flow path 36 such as a pipe for supplying and discharging the vibration member 40 is connected.

  The flow path 36 in the vicinity of the transmission case 8 is provided with a pressure feeding part 37 such as a hydraulic pump, and the flow path switching valve connected to the transmission case 8 is provided on the cylinder liner 33 side (downstream side) in the vicinity of the pressure feeding part 37. 42 is provided. Further, a check valve 43 is provided between the flow path switching valve 42 and the cylinder liner 33, and the flow path 36 branched from the flow path 36 located on the cylinder liner 33 side of the check valve 43 includes: An accumulator 46 is connected via a check valve 44 and a throttle 45.

  Next, a relief valve 38 is provided in the flow path 36 that branches from the flow path 36 between the check valve 43 and the flow path switching valve 42 and returns to the mission case 8. The flow path switching valve 42 and the vibration detector 35 are connected to a controller 39 such as a controller.

  By the vibration isolator 31 including the power reduction means 47 configured by the vibration detector 35, the control unit 39, the flow path switching valve 42, the check valves 43 and 44, and the accumulator 46, The hydraulic oil (lubricating oil) as the vibration isolating member 40 included in the transmission case 8 or the like is driven into the cylinder liner 33 by driving of the hydraulic pump 37 until the pressure in the cylinder s reaches the oil pressure set in advance by the relief valve 38. Then, the piston 32 is pushed up by the hydraulic oil, and the upper body 1A is supported by the piston 32.

  When the upper body 1A to be isolated from vibrations input to the body due to road surface irregularities and propagating from the lower body 1B during vibrations, the lower body integral with the cylinder liner 33 is used. When 1B is the axial direction of the cylinder s and is oscillated upward or downward, and the upward or downward force is applied to the piston 32 from the hydraulic oil, the relief valve 38 is operated to supply the hydraulic oil in the cylinder s. By discharging, the pressure in the cylinder s is kept constant, and the upper body 1A is vibrated.

  Here, when the vibration applied to the airframe is low vibration (small amplitude), a method for reducing the power of the vibration isolation unit 31 by the power reduction means 47 and isolating the upper body 1A will be described.

  As shown in FIG. 5, the vibration detector 35 detects that low vibration below an appropriately set vibration is applied to the airframe, and the detection information is transmitted to the control unit 39. Next, the control unit 39 switches the flow path switching valve 42 based on the detection information, so that the pressure feeding of the vibration isolating member 40 from the pressure feeding section 37 is blocked by the flow path switching valve 42 and the check valve 43. The anti-vibration member 40 in the flow path 36 up to the back flows and is discharged into the mission case 8.

  At this time, the vibration isolation member 40 is discharged directly from the pressure feeding unit 37 to the mission case 8. At that time, the discharge pressure of the vibration isolation member 40 increases. By utilizing this discharge pressure for the pilot of the check valve 44, the check valve 44 can be reversely flowed. On the contrary, the anti-vibration member 40 discharged from the relief valve 38 to the mission case 8 is reduced, so that the check valve 43 that uses this discharge pressure for the pilot cannot flow backward. That is, the upper body 1A is balanced and supported by the air pressure inside the accumulator 46, and the upper body 1A is supported in a vibration-proof manner by the air spring effect of the accumulator 46. Further, by inserting the throttle 45 in the flow path 36 to the accumulator 46 and limiting the flow rate of the vibration isolation member 40, the damping effect is improved and the vibration isolation performance of the upper body 1A is improved.

  It should be noted that a large force is applied to the airframe during the vibration isolating operation of the low vibration by the power reducing means 47 of the anti-vibration unit 31, and a large vibration (large amplitude) greater than the vibration set as appropriate is detected by the vibration detector 35. In this case, the control unit 39 switches the flow path switching valve 42 based on this detection information, so that the vibration isolation member 40 passes through the relief valve 38. At this time, since the discharge pressure of the vibration isolation member 40 discharged from the relief valve 38 to the mission case 8 increases, this can be used for a pilot to allow the check valve 43 to flow backward. At that time, the check valve 44 cannot be backflowed because its pilot pressure is reduced. That is, the normal vibration isolation method using the pressure feeding unit 37 is switched.

The power reduction means 47 can also change its arrangement. FIGS. 6 to 7 are schematic side views of the vibration isolator showing an example of changing the configuration of the power reducing means. First, as shown in FIG. 6, a flow path switching valve 42a is provided in the flow path 36 between the relief valve 38 and the cylinder liner 33, and the accumulator 46 is connected to the mission case 8 via the flow path switching valve 42a. Connected. As described above, the vibration detector 35 and the flow path switching valve 42a are connected to the control unit 39.

  Here, as described above, when the vibration detector 35 detects the low vibration applied to the airframe, the flow switching valve 42a is switched by the control unit 39, so that the pressure feeding unit in the flow switching valve 42a. The pressure of the vibration isolator 40 from 37 is blocked, and the air in the accumulator 46 presses the vibration isolator 40 in the cylinder liner 33 from the flow path switching valve 42a via the flow path 36. The upper body 1A is in a vibration-proof state due to the air spring effect of the accumulator 46.

  As described above, when a large amplitude is detected by the vibration detector 35 during the vibration isolating operation of low vibration, the control unit 39 switches the flow path switching valve 42a based on this detection information, thereby The normal pressure using the pressure feeding unit 37 is used to block the air pressure supply from the accumulator 46 at the path switching valve 42a and pump the vibration isolating member 40 from the pressure feeding unit 37 into the cylinder liner 33 through the flow path switching valve 42a. Switch to anti-vibration method.

  Next, in FIG. 7, the flow path 36 is branched and connected to the upper and lower sides of the cylinder liner 33 with the piston head 32a interposed therebetween, and the accumulator 46 is connected to the flow path switching valve via the flow path switching valve 42b. 42 b and the flow path 36 between the relief valve 38. As described above, the vibration detector 35 and the flow path switching valve 42 b are connected to the control unit 39.

  Here, as described above, when the vibration detector 35 detects low vibration, the flow switching valve 42b is switched by the control unit 39, so that the vibration isolating member 40 from the pressure feeding unit 37 is switched in the flow switching valve 42a. Is shut off. At this time, since the air pressure in the accumulator 46 is substantially equal to the set pressure of the relief valve 38, that is, the pressure of the vibration isolator 40 in the cylinder s, the piston 32 becomes large when the flow path switching valve 42b is switched. Do not move. That is, the upper body 1A can be changed to a vibration-proof state using the air spring of the accumulator 46 without causing an impact due to the flow path switching.

  In FIG. 7, the anti-vibration member 40 is also provided in the upper part of the cylinder liner 33 with the piston head 32a interposed therebetween, but the anti-vibration member 40 may be provided only in the lower part. As described above, when a large amplitude is detected by the vibration detector 35 during the vibration-proof operation of low vibration, the control unit 39 switches the flow path switching valve 42b on the basis of this detection information. Normal using the pressure feeding unit 37, which shuts off the air pressure supply from the accumulator 46 in the flow path switching valve 42b and pumps the vibration isolator 40 from the pressure feeding part 37 into the cylinder liner 33 through the flow path switching valve 42b. It can be switched to the vibration isolation method.

  Next, the power reduction means can also operate the vibration isolator 31 using the pressure of the accumulator 46 during a large vibration. FIG. 8 is a schematic side view of a vibration isolator having power reducing means for compensating the inside of a cylinder using an accumulator.

  In this case, an accumulator 46 provided via a check valve 41a is provided in the flow path 36 connected to the cylinder liner 33 below the piston head 32a, in which the pressure feeding part 37 and the flow path switching valve 42d are provided. The flow path 36 branched from the flow path 36 is connected to the transmission case 8 via the cylinder liner 33 and the flow path switching valve 42d above the piston head 32a. A relief valve 38c, a low pressure relief valve 38d, and check valves 41b, 41c, 41d are provided. Further, the vibration detector 35 and the flow path switching valve 42d are connected to the control unit 39.

  Here, at the time of normal vibration isolation, the vibration isolation member 40 by the pressure feeding unit 37 is supplied to the cylinder s via the flow path switching valve 42d, and the upper body 1A is isolated by the operation of the vibration isolation unit 31, and the accumulator The pressure is increased by the anti-vibration member 40 in the flow path 36 via the check valve 41a. In addition, a vibration isolating member 40 having a low pressure that does not affect the support of the upper body 1A is sealed in the upper portion of the cylinder liner 33. This pressure is set by the relief valve 38d. When the vibration detector 35 detects that the vibration applied to the airframe is small, the control unit 39 switches the flow path switching valve 42d, and the flow path switching valve 42d blocks the supply of the vibration isolating member 40 by the pressure feeding unit 37. .

  At this time, when a large vibration is applied and the piston 32 moves upward, the vibration isolating member 40 flows through the check valve 41c, so that the check valve 41a can flow back as a pilot. In this state, since the piston 32 is moved upward, the pressure of the vibration isolating member 40 below the cylinder liner 33 is reduced. This pressure drop is compensated by the air pressure of the accumulator 46. By repeating this state, the air pressure of the accumulator 46 gradually decreases, and the vibration isolation performance decreases accordingly. For this reason, when the vibration detector 35 detects a vibration of a certain threshold value or more, the control unit 39 switches the flow path switching valve 42d to return to the normal vibration-proof state and boosts the accumulator 46. To do.

  The method of operating the vibration isolator 31 using the pressure of the accumulator 46 during the large vibration described above can be configured as shown in FIG. FIG. 9 is a schematic side view of the vibration isolator showing another example of the power reducing means for compensating the cylinder using the accumulator.

  In this case, an accumulator is connected to the flow path switching valve 42e provided in the flow path 36 connected to the cylinder liner 33 below the piston head 32a and between the pressure feeding portion 37 and the relief valve 38e. And a relief valve 38 f is provided in the flow path 36 between the flow path switching valve 42 e and the accumulator 46. Further, the vibration detector 35 and the flow path switching valve 42e are connected to the control unit 39.

  Here, as described above, in the normal vibration isolation state, the vibration isolation member 40 is supplied to the cylinder s by the pressure feeding unit 37 via the flow path switching valve 42e. At this time, when the vibration detector 35 detects that the vibration is low, the flow path switching valve 42e is once switched to the central portion in the figure, and the accumulator 46 is boosted for a set time. After boosting the accumulator 46, the flow path switching valve 42e is switched again so that the vibration isolator 40 supplied from the pressure feeding unit 37 returns directly to the mission case 8. In this case, the accumulator 46 is connected to the lower part of the cylinder s. At this time, a vibration isolating state using the air pressure inside the accumulator 46 is established. In this configuration, after absorbing several vibrations, the air pressure inside the accumulator 46 is lowered, and the vibration isolation performance is lowered. When the vibration detector 35 detects vibration exceeding the threshold value, the vibration detector 35 returns to the normal vibration-proof state in which the pressure feeding unit 37 and the cylinder liner 33 are connected to each other. Thereafter, this switching mechanism is repeated.

  Next, the power reducing means 47 ′ may be provided with an elastic body on the piston 32 of the cylinder s of the vibration isolator 31. FIG. 10 is a schematic side view of a vibration isolator having power reducing means in which an elastic body is provided on a piston of a cylinder.

  The power reducing means 47 ′ is provided in the cylinder liner 33, for example, an elastic body 50 such as a spring attached to the lower end portion of the piston head 32 a and the piston 32 attached to the lower end portion of the elastic body 50. The free piston 48 is configured to be slidable in accordance with the sliding. Further, a flow passage 49 of the vibration isolation member 40 provided in the cylinder liner 33 is provided inside the middle portion of the cylinder liner 33.

  The cylinder liner 33 below the free piston 48 in such a cylinder s is connected to a flow path 36 provided with a pressure feeding portion 37, a relief valve 38, and a flow path switching valve 42, and above the piston head 32a. The flow path 36 connected to the cylinder liner 33 is connected to a flow path switching valve 42. The vibration detector 35 and the flow path switching valve 42 are connected to the control unit 39.

  Here, when the vibration applied to the airframe by the vibration detector 35 is large, the upper body 1 </ b> A is vibrated by the operation of the cylinder s by the vibration-proof member 40 using the pressure-feeding portion 37. In the cylinder liner 33, the space s1 above the piston head 32a, the space s2 between the piston head 32a having the elastic body 47 and the free piston 48, and between the free piston 48 and the cylinder liner 33 bottom. Anti-vibration members 40 are introduced into the spaces s3.

  Next, when vibration applied to the airframe by the vibration detector 35 is small, the control unit 39 switches the flow path switching valve 42 so that the vibration isolating member 40 supplied from the pressure feeding unit 37 is the flow path switching valve 42. Blocked. The sliding of the cylinder liner 33 due to small vibrations is absorbed by the expansion and contraction of the elastic body 50, and a damping action is obtained by moving the vibration isolating members 40 in the spaces s1 and s2 through the flow passages 49. Thus, the vibration reduction effect is improved. At this time, the vibration isolating member 40 is supplied from the pressure feeding unit 37 to the space s1. When the vibration isolating member 40 reaches the flow path 36 provided above the flow path 36, the mission case 8 starts from here. Is discharged. In this state, the vibration isolating member 40 supplied from the pressure feeding unit 37 does not work for vibration isolation by the cylinder s when the vibration applied to the airframe is small. Therefore, the power of the pressure feeding unit 37 can be reduced.

  When the vibration applied to the airframe is large, the cylinder liner 33 is slid up and down to some extent, so that the position of the flow passage 49 is shifted from the side of the piston head 32a and the vibration isolation between the space s1 and the space s2 is performed. The traffic of the member 40 is closed. For this reason, the internal pressure of the vibration isolating member 40 supplied to the space s3 by the pressure feeding unit 37 is held constant by the relief valve 38, and the upper body 1A is vibrated.

  With the above-described configuration, when the vibration applied to the airframe is small, the elastic body 47 in the piston 32 is expanded and contracted and the cylinder liner 33 is moved from the operation of the cylinder s by the vibration isolating member 40 by the pressure feeding unit 37. Since the upper body 1A is vibration-isolated by switching to the operation of the cylinder s by the movement of the vibration-isolating member 40 between the space s1 and the space s2, the vibration-isolating member 40 by the pressure-feeding portion 37 does not work, so Power can be reduced.

  In the anti-vibration part 31 provided with the above power reduction means 47 and 47 ', the anti-vibration performance can be improved. FIG. 11 is a schematic side view of a cylinder having a rotation mechanism at the upper part of the piston (a), a schematic side view of a cylinder having the rotation mechanism at the lower part of the cylinder liner, and FIG. FIG. 13 is a schematic side view of a cylinder showing a rotation mechanism in which a piston is integrated with a motor.

  As described above, the vibration isolating portion 31 keeps the internal pressure of the cylinder s constant with the sliding of the cylinder s due to the vibration applied to the lower body 1B. The body 1A is anti-vibrated, but at this time, a frictional force is generated between the piston 32 in the cylinder s and the sealing material 51 made of the cylinder liner 33, fluororesin, or the like, and the anti-vibration effect by the anti-vibration unit 31 is reduced. To do. In particular, at the time of low vibration, the relative displacement between the piston 32 and the cylinder liner 33 cannot be obtained, and a static friction state is generated, so that a large frictional force is generated. By making this a dynamic friction state, it is possible to improve the anti-vibration effect even during low vibration.

  Therefore, first, as shown in FIG. 11A, for example, a rotation mechanism 52 that rotates the piston 32, which will be described in detail later, is provided between the upper body 1A and the piston 32 in the cylinder s. By rotating the cylinder liner 33 in the horizontal direction, the piston 32 and the cylinder liner 33 are slid in the axial direction when the vibration isolator 31 is operated. The sliding surface becomes dynamic friction, and the frictional force between them becomes small.

  As a result, since the piston 32 and the cylinder liner 33 are smoothly slid in the axial direction when the vibration isolator 31 is operated, vibration is not propagated in the cylinder s, and the vibration isolating performance is improved. .

  As shown in FIG. 11B, for example, a rotation mechanism 52 ′ for rotating the cylinder liner 33 may be provided at the bottom of the cylinder liner 33. In this case, since the cylinder liner 33 is rotated in the horizontal direction, the piston 32 and the cylinder liner 33 are slid in the axial direction when the vibration isolator 31 is operated. Then, the sliding surface with the cylinder liner 33 becomes kinetic friction, the frictional force between them becomes small, and the same effect as described above can be obtained. In addition, by providing the flow path 36 in the shaft core at the bottom of the cylinder liner 33, the vibration isolating member 40 in the cylinder liner 33 can be supplied and discharged. The installation positions of the rotation mechanisms 52 and 52 ′ are not limited to the above.

  Next, the configuration of the rotating mechanism will be described by taking the rotating mechanism 52 that rotates the piston 32 as an example. First, as shown in FIG. 12, for example, a gear 54 is attached to a motor shaft 53 a of a motor 53 installed at the bottom of the upper body 1 </ b> A, and the gear 54 is meshed with a gear 55 fitted to the top of the piston 32. The motor 53 is preferably driven by power supply from a battery (not shown). Reference numeral 56 denotes a ball bearing.

  With such a configuration, the piston 32 is forcibly rotated by the driving force of the motor 53 via the gears 54 and 55, so that the piston 32 is always stably rotated, and the piston 32 and the cylinder liner 33 slide. The surface can be reliably brought into a dynamic friction state.

As shown in FIG. 13, for example, the piston 32 may be integrated with the motor 53 by fixing the upper end of the piston 32 to the motor shaft 53 a of the motor 53 installed at the bottom of the upper body 1 </ b> A. As a result, without the need for intermediate member such as a gear 54, 55 for transmitting power from the motor 53 to the piston 32 by rotation of the piston 32 to which the power is transmitted to the high efficiency directly from the motor 53, stabilizing the piston 32 at all times The sliding surfaces of the piston 32 and the cylinder liner 33 can be surely brought into a dynamic friction state.

  Next, the power of the rotating mechanism can be reduced. FIG. 14 is a schematic side view of a cylinder that performs rotation control of the rotation mechanism according to the magnitude of vibration, and FIG. 15 is a schematic side view of the cylinder that rotates the rotation mechanism according to the discharge flow rate of the vibration isolation member from the relief valve.

  First, the vibration detector 35 and the motor 53 attached to appropriate positions of the upper body 1A and the lower body 1B as shown in FIG. Here, based on the detection information detected by the vibration detector 35 that a vibration equal to or greater than the vibration (amplitude) set as appropriate is applied to the airframe, the control unit 39 rotates the motor 53, The sliding surface with the cylinder liner 33 is brought into a dynamic friction state. Further, when larger vibrations occur, the relative displacement between the piston 32 and the cylinder liner 33 increases, and accordingly, a dynamic friction state automatically occurs, so that the driving of the motor 53 is stopped. Further, based on the detection information detected by the vibration detector 35 that the vibration equal to or less than the vibration (amplitude) set as appropriate in the airframe is applied, or the vibration is not applied, the controller 39 causes the motor 53 to Stop driving.

  As a result, when the vibration applied to the airframe is relatively small and large, it is not necessary to rotate the piston 32 at all times by stopping the motor 53 and stopping the rotation of the piston 32, thereby improving the durability of the motor 53 and Power can be reduced. Accordingly, the relative displacement between the piston 32 and the cylinder liner 33 cannot be obtained, and the motor 53 is driven only in a limited state where the sliding surface is in a static friction state. Can be reduced. The power reduction of the rotation mechanisms 52 and 52 'is performed when the rotation mechanism 52 is provided at the upper part of the cylinder s as described above, when the rotation mechanism 52' is provided at the lower part of the cylinder s, or at other appropriate positions. Applies to every case you have.

  Further, the motor 53 can be driven by using the discharge flow rate of the vibration isolation member 40 from the relief valve 38. In this case, as shown in FIG. 16, the pressure motor 53 ′ (fluid drive motor) fixed to the upper end of the piston 32 and installed in the upper body is connected to the discharge port of the relief valve 38 by piping or the like. The Since the pressure motor 53 ′ (fluid drive motor) is a known technique, detailed description thereof is omitted.

  Here, vibration is applied to the airframe, and when the vibration isolating member 40 in the cylinder liner 33 is discharged from the relief valve 38 as the cylinder s slides during the operation of the vibration isolating portion 31, this is discharged. When the vibration isolator 40 flows into the pressure motor 53 ′, the pressure motor 53 ′ is driven, the piston 32 rotates, and the sliding surface between the piston 32 and the cylinder liner 33 enters a dynamic friction state. In particular, since the anti-vibration effect is reduced as the discharge amount of the anti-vibration member 40 increases, in such a situation, the sliding surface between the piston 32 and the cylinder liner 33 can be effectively brought into a dynamic friction state. it can.

  As a result, when there is little vibration applied to the airframe and the discharge flow rate of the vibration isolating member 40 from the relief valve 38 is small, the drive of the pressure motor 53 'can be stopped, and the durability of the pressure motor 53' is improved and the power is reduced. can do. Further, it is not necessary to separately provide a device for controlling the driving of the rotating mechanisms 52 and 52 ′, and the power of the rotating mechanisms 52 and 52 ′ can be reduced with a simple configuration.

  The wheel type tractor has been described above as an example of an industrial machine. However, the present invention is not limited to this. The present invention is not limited to this. It can be applied to all industrial machines with parts to be vibration-proofed such as aircraft and ships, as well as vehicles such as snow blowers and ambulances.

  Further, the vibration isolator 31 is not limited to the above-described anti-vibration of the upper body 1A of the fuselage, and for example, a suspension provided with a control unit, a cabin, etc. on the lower body 1B of the fuselage. The present invention can also be applied to any industrial machine such as a lowering monorail that has a portion to be damped, for example, in the lower body 1B of the airframe.

  The vibration isolating member 40 is not limited to the hydraulic oil (lubricating oil) as described above, and air that has taken in outside air or the like in the vibration isolating section 31 may be used.

  As described above in detail, the tractor 1 (industrial machine) of this example includes the vibration isolating unit 31 between the upper body 1A and the lower body 1B constituting the airframe, and the vibration isolating unit 31 includes the pressure feeding unit 37 and the relief. A cylinder liner 33 connected to a flow path 36 provided with a valve 38 and capable of supplying and discharging the vibration isolating member 40, and the inside of the cylinder liner 33 are slidable, and one end thereof is attached to the upper body 1A or the lower body 1B. The vibration isolation member 40 is supplied to and discharged from the cylinder liner 33 according to the direction and amplitude of vibration propagating from the upper body 1A or the lower body 1B. In an anti-vibration device for an industrial machine that maintains the internal pressure of the cylinder liner 33 constant before and after the vibration load by adjusting the amount of the vibration member 40 to prevent vibration of the upper body 1A or the lower body 1B. Part 31, to reduce the driving force of the vibration isolating unit 31, in which provided with a power reducing means 47,47'.

  In addition, the power reduction means 47 is provided with a flow path switching valve 42, 42a, 42b, 42d, 42e, and an accumulator 46 in the flow path 36 between the pressure feeding unit 37 and the cylinder liner 33, and in the airframe. Includes a vibration detector 35 that detects vibration of the airframe, and connects the flow path switching valves 42, 42 a, 42 b, 42 d, 42 e and the vibration detector 35 to the control unit 39. Further, the power reducing means 47 ′ sandwiches the elastic body 50 in the piston 32, and includes a flow path switching valve 42 in the flow path 36 between the pressure feeding portion 37 and the cylinder liner 33, and the airframe vibrates. A detector 35 is provided, and the flow path switching valve 42 and the vibration detector 35 are connected to the control unit 39.

  Further, the cylinder s includes rotation mechanisms 52 and 52 ′ that rotate the cylinder s, and the rotation mechanisms 52 and 52 ′ and the vibration detector 35 are connected to the control unit 39 or the rotation mechanisms 52 and 52. 'Is driven by the discharge flow rate of the vibration isolation member 40 discharged from the relief valve 38.

FIG. 1 is a left side view of a wheeled tractor as a work vehicle showing an embodiment of an industrial machine including an upper body and a lower body according to the present invention. It is a top view of the tractor. It is the perspective view which looked at the tractor provided with a vibration isolator from the front. It is a schematic diagram which shows the installation position of a vibration isolator. It is a side surface schematic diagram of the vibration isolator which shows an example of the power reduction means in a vibration isolator. It is the side surface schematic diagram of the vibration isolator which showed the example of a change of the structure arrangement | positioning of a power reduction means. It is the side surface schematic diagram of the vibration isolator which showed the example of a change of the structure arrangement | positioning of a power reduction means. It is a side surface schematic diagram of a vibration isolator provided with the power reduction means which supplements the inside of a cylinder using an accumulator. It is a side surface schematic diagram of the vibration isolator which shows another example of the power reduction means which supplements a cylinder using an accumulator. It is a side surface schematic diagram of the vibration isolator provided with the power reduction means which provided the elastic body in the piston of a cylinder. It is the side surface schematic diagram (a) of a cylinder provided with a rotation mechanism in a piston upper part, and the side surface schematic diagram (b) of a cylinder provided with a rotation mechanism in a cylinder liner lower part. It is a side surface schematic diagram of the cylinder which shows the rotation mechanism which rotates a piston by the gear drive by a motor. It is a side surface schematic diagram of the cylinder which shows the rotation mechanism which integrated the piston with the motor. It is a side surface schematic diagram of the cylinder which performs rotation control of a rotation mechanism with the magnitude | size of a vibration. It is a side surface schematic diagram of the cylinder which rotates a rotation mechanism with the discharge flow volume of the vibration proof member from a relief valve.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1A Upper body 1B Lower body 2 Body frame 8 Mission case 9 Cabin 31 Vibration isolator 32 Piston 32a Piston head 33 Cylinder liner 35 Vibration detector 36 Flow path 37 Pressure feeding part 38, 38a, 38b, 38c, 38d, 38e, 38f Relief Valve 39 Control unit 40 Anti-vibration member 41a, 41b, 41c, 41d, 43, 43 ', 44, 44' Check valve 42, 42a, 42b, 42d, 42e Flow path switching valve 46 Accumulator 47, 47 'Power reduction means 50 Elastic body 51 Sealing material 52, 52 'Rotating mechanism 53 Motor 53' Pressure motor s Cylinder s1, s2, s3 Space

Claims (6)

  A cylinder liner provided between the upper body and the lower body constituting the airframe, wherein the vibration isolation unit is connected to a flow path provided with a pressure feeding unit and a relief valve, and is capable of supplying and discharging a vibration isolation member; A cylinder comprising a piston which is slidable in the cylinder liner and has one end attached to the upper body or the lower body, and depending on the direction and amplitude of vibration propagating from the upper body or the lower body The cylinder liner is supplied and discharged with the vibration isolation member, and the amount of the vibration isolation member in the cylinder liner is adjusted to keep the internal pressure of the cylinder liner constant before and after the vibration load. In the vibration isolating apparatus for an industrial machine that vibrates the upper body or the lower body, the vibration isolating unit includes a power reduction unit that reduces an overload of the driving force of the vibration isolating unit at a low vibration below a set vibration. That Anti-vibration device of industrial machinery to be butterflies.   The power reducing means includes, in the flow path between the pressure feeding section and the cylinder liner, a flow path switching valve that passes or blocks the vibration isolating member by the pressure feeding section, and one accumulator. The said airframe is provided with the vibration detector which detects the vibration of the said airframe, The said flow-path switching valve and the said vibration detector are connected to a control part, The control part of Claim 1 characterized by the above-mentioned. Vibration isolator for industrial machinery. The power reducing means includes an elastic body attached to a piston head of the piston in the cylinder liner, and includes the flow path switching valve in the flow path between the pressure feeding unit and the cylinder liner. The vibration isolator for an industrial machine according to claim 2 , wherein the machine body includes the vibration detector, and the flow path switching valve and the vibration detector are connected to the control unit.   The vibration isolator for an industrial machine according to claim 1, wherein the cylinder includes a rotation mechanism that rotates the cylinder. The vibration isolator for an industrial machine according to claim 4 , wherein the rotation mechanism and the vibration detector are connected to the control unit. 5. The vibration isolator for an industrial machine according to claim 4 , wherein the rotation mechanism is driven by a discharge flow rate of the vibration isolation member from a relief valve that adjusts an internal pressure of the cylinder liner.

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