JP3672655B2 - Swivel work vehicle - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
  The present invention relates to an improvement of a variable displacement hydraulic piston pump portion for realizing compactness in constituting a compact type turning work vehicle.
[0002]
[Prior art]
  Along with the recent shortage of manpower and labor reduction, the demand for a small-sized swivel work vehicle with excellent turning performance is increasing.
  In order to reduce the size of the main body, the configuration in which the engine is installed in the bonnet of the main body and the variable displacement hydraulic piston pump is disposed directly on the flywheel is also disclosed in Japanese Patent Application No. Hei 7 -172456. The structure of a hydraulic piston pump provided with a plurality of discharge ports is also disclosed in Japanese Patent Laid-Open No. 6-123277.
[0003]
[Problems to be solved by the invention]
  The subject of this invention demonstrates the subject regarding the variable displacement hydraulic piston pump (henceforth hydraulic pump P) attached to an engine in a turning type work vehicle.
  First, problems related to the direct connection structure between the pump shaft and the flywheel will be described with reference to FIGS. 2, 23, and 24. 2 is a plan view of the main body 3 showing the internal structure of the bonnet 4, FIG. 23 is a front partial sectional view showing a direct connection structure between the conventional hydraulic pump P and the flywheel housing FWH, and FIG. 24 is another conventional hydraulic pressure. It is a front fragmentary sectional view which shows the direct connection structure of the pump P and the flywheel housing FWH.
[0004]
  Conventionally, for example, as shown in JP-A-6-123277, a structure in which a coupling portion C ′ to a flywheel FW ′ attached to a pump shaft PS protrudes somewhat toward the hydraulic pump P from the flywheel FW ′. (As shown in FIG. 23 and FIG. 24, this protrusion width is L2.) In addition, the pump mount PM ′, which is a pump-side housing engaged with the flywheel housing FWH, is also hydraulically The shape bulges to the pump P side, that is, a shape in which the central portion is projected from the hydraulic pump P side.
[0005]
  In such a connection structure, the protruding width L2 is included in the lateral width L1 from the tip of the hydraulic pump P to the end surface of the flywheel FW 'on the hydraulic pump P side. The protruding width L2 of the coupling portion C ′ can be reduced if the coupling portion C ′ is completely fitted in the flywheel FW ′. If this portion is reduced, the distance L1 can be shortened. This is because the distance L from the front end of the radiator R on the upper side of the engine E shown in FIG. 2 to the front end of the hydraulic pump P arranged in series on the lower side of the engine. This leads to shortening of the bonnet 4 containing these, and is effective in reducing the turning radius to less than half of the vehicle width between the left and right crawler parts 10a and 10a. Therefore, it is possible to provide a revolving work vehicle that is excellent in performance.
[0006]
[Means for Solving the Problems]
  The present invention uses the following means in order to solve the above-described problems and provide a good turning work vehicle.
  According to the first aspect of the present invention, in the configuration in which the pump shaft PS of the variable displacement hydraulic piston pump P is directly connected to the flywheel FW of the engine E mounted on the main body of the turning work vehicle, the variable displacement hydraulic pressure is set. A coupling portion C is attached to and engaged with the tip of the pump shaft PS protruding from the piston pump P, and the coupling portion C is internally fitted in the insertion hole FWa of the flywheel FW. C and the flywheel FW are configured to be fixed, and the coupling portion C of the pump shaft PS is completely fitted in the insertion hole FWa of the flywheel FW.Is.
[0007]
  According to a second aspect of the present invention, the shape of the pump mount PM that engages and fixes the variable displacement hydraulic piston pump P to the flywheel housing FWH is the center of the variable displacement hydraulic piston pump. When the fixed part with P is moved to the flywheel FW side, and the fixed side with the flywheel housing FWH on the outer peripheral part is directed to the variable displacement hydraulic piston pump P side, the pump is The central part of the mount PM is configured to be concave.Is.
[0008]
DETAILED DESCRIPTION OF THE INVENTION
  Embodiments of the present invention will be described with reference to the drawings. 1 is an overall side view of a swivel work vehicle, FIG. 2 is a plan view of a main body 3 showing the internal configuration of a bonnet 4, FIG. 3 is a side view of a dual-function pedal 1, and FIG. FIG. 5 is a front view when the pedal cover 2 is opened, FIG. 6 is a side view of the dual function pedal 1 ′, FIG. 7 is a plan view when the pedal cover 2 ′ is covered, and FIG. FIG. 9 is a front view when the pedal cover 2 ′ is opened, and FIG. 10 is a partial plan view showing an assembly configuration of the PTO driving pedal portion 1′b in the dual function pedal 1 ′. FIG. 11 is a partial side view showing the rotational configuration of the PTO driving pedal portion 1′b in the dual function pedal 1 ′, FIG. 12 is a front view showing the direct connection configuration of the hydraulic pump P to the flywheel housing FWH, and FIG. Suction oil pipe for hydraulic pump P 14 is a side view schematically showing the piping direction of the discharge oil pipe, FIG. 14 is a schematic side view of the main body 3 showing the piping direction in the bonnet 4, and FIG. 15 is a diagram showing the suction discharge port housing PH attached to the hydraulic pump P. ) Is a side view, (b) is a front view, FIG. 16 is a sectional view taken along line XX in FIG. 15 (b), and FIG. 17 is attached with a suction / discharge port housing PH having a discharge port DP drilled in the pump axial direction. 18 is a perspective view of the hydraulic pump P. FIG. 18 shows the piping direction in the bonnet 4 when the hydraulic pump P assembled with the suction / discharge port housing PH having the discharge port DP formed on the same side as the suction port SP is used. 3 is a schematic side view of the main body 3.
[0009]
  The overall configuration of the turning work vehicle will be described with reference to FIGS. 1 and 2. 1 and 2 show a swivel excavator, in which the turning radius is set to approximately half or less of the vehicle width, and the space for disposing the operation tools is limited. The main body 3 is rotatably mounted on a crawler traveling device 10 having left and right crawlers 10a and 10a, and a working arm made up of a boom 7, an arm 8 and a bucket 9 is formed at the front end of the main body 3. Has been. In the main body 3, a bonnet 4 containing an engine or the like is formed in a rear part from the center, and a seat 6 is mounted on the bonnet 4. It is installed. A pedal step plate 3b is laid on the upper surface of the main body on both sides of the front column 6 in front of the step 3a. The boom 7 is provided with a hydraulic port 7a for PTO driving.
[0010]
  Next, a configuration relating to a variable displacement hydraulic piston pump that is directly connected to an engine E installed in the hood B, that is, a hydraulic pump P will be described. The hydraulic pump P is provided with a bush between its fixed swash plate and its support so that the fixed swash plate can be moved. When the engine is overloaded, the intake hydraulic pressure is reduced. The fixed swash plate is configured to naturally move to a position where the discharge pressure is reduced by rising. Therefore, the engine E can be used with a small capacity, and moreover, it has a plurality of discharge ports DP and is a multiple hydraulic pump, which is a fixed capacity type and has a single discharge port connected in series. A function equivalent to the above-described state can be exhibited by one hydraulic pump P. Therefore, since the lateral width L from the radiator R to the front end of the hydraulic pump P described in the above-mentioned prior art is a fixed capacity type, a hydraulic pump having one discharge port is connected, and the fixed capacity is used, the large capacity engine Compared to the previous configuration that needed to, it has been significantly shortened.
[0011]
  The direct connection structure of the pump shaft PS of the hydraulic pump P shown in FIG. 12 and the flywheel FW on the output side of the engine E is for further shortening the lateral width L to obtain better turning performance. Is. This will be described.
  A coupling portion C is attached to the tip of the pump shaft PS, and the coupling portion C is directly connected by being fitted inside the flywheel FW. Part of the part C ′ protruded from the flywheel FW ′ to the hydraulic pump P side. In the configuration shown in FIG. 12, this is because the coupling portion C of the flywheel FW is fitted into the flywheel FW so that the coupling portion C is completely (that is, does not protrude). The insertion hole FWa is taken deeper than before. On the other hand, in the coupling portion C, a recess Ca is provided to avoid interference with the fastening bolt 16 with respect to the engine output shaft ES of the flywheel FW.
[0012]
  Further, as the coupling portion C is completely fitted in the flywheel FW as described above, the shape of the pump mount PM including the pump shaft PS to be engaged with the flywheel housing FWH is shown in FIG. As described above, the central portion is brought closer to the flywheel FW side (engine E side), that is, when viewed from the hydraulic pump P, the central portion of the pump mount PM is recessed. Conventionally, as shown in FIG. 23 or FIG. 24, the center portion of the pump mount PM ′ is protruded from the hydraulic pump P by an amount corresponding to the protrusion of the pump shaft PS (protrusion width L 2).
[0013]
  As described above, by completely fitting the coupling C of the pump shaft PS into the flywheel FW and making the shape of the pump mount PM as described above, the conventional protrusion width L2 is eliminated, and the hydraulic pressure is reduced. The lateral width L1 from the tip end of the pump P to the end face of the flywheel FW on the hydraulic pump side is shortened by the amount corresponding to the removal of the protruding width L2. Accordingly, as shown in FIG. 2, the lateral width L from the radiator R to the engine E, the flywheel housing FWH, and the hydraulic pump P in the bonnet 4 is also shortened by the shortening of the lateral width L1. The lateral width of the bonnet 4 can be further shortened, that is, the turning radius can be shortened.
[0014]
  Next, as another problem in the hydraulic pump P, there is an arrangement structure of the suction / discharge oil pipes. This will be described with reference to FIGS. FIG. 25 is a side view showing the piping direction of the suction / discharge oil pipe in the conventional hydraulic pump P, FIG. 26 is a schematic side view of the main body 3 showing the piping direction of the suction / discharge oil pipe in the bonnet 4, and FIG. It is a figure which shows suction / discharge port housing PH ', (a) is a side view, (b) is a front view, FIG. 28 is X'-X' sectional view taken on the line in FIG.27 (b). In addition, the arrow in FIG.25 and FIG.26 and the white arrow in FIG.27 and FIG.28 show the direction of pressure oil flow.
[0015]
  As shown in FIG. 24, a suction / discharge port housing PH ′ is attached to the tip of the hydraulic pump P, and a suction port SP and a discharge port DP formed in the suction / discharge port housing PH ′. The suction oil pipe ST and the discharge oil pipe DT are connected to '. These pipes are installed in the bonnet 4 as shown in FIGS. 25, 27 (a), and 28, and the relative piercing between the conventional suction port SP and the discharge port DP ′ is performed. The installation angle is 180 °. In this structure, as shown in FIG. 26, particularly in the small bonnet 4 in the turning work vehicle, the discharge pressure oil pipe DT connected to the discharge port DP ′ interferes with the bonnet 4. In order to avoid this interference, the bonnet must be avoided. Thus, the interference part 4 had to be shaped to bulge out, which prevented compactness.
[0016]
  Next, an embodiment relating to the drilling position of the discharge port DP in the suction discharge port housing PH attached to the hydraulic pump P will be described with reference to FIGS. 13, 14, 17, and 18 and the white arrows in FIGS. 15 and 16 indicate the direction of pressure oil flow. First, the position of the suction port SP is the same as that of the conventional suction port SP, that is, the suction port SP of the conventional suction / discharge port housing PH '. With regard to the discharge port DP, as shown in FIG. 28, in the conventional suction discharge port housing PH ′, a waste hole DP′a necessary for processing to connect the discharge ports DP ′ and DP ′ to the discharge oil passages DR and DR. DP′a opens to the outside at an angle θ (<180 °) with the suction port SP. In the hydraulic pump P shown in FIGS. 13 to 16, the conventional discard holes DP'a and DP'a are utilized as they are as the discharge ports DP and DP. Conventionally, the discharge ports DP ′ and DP ′ are formed so as to intersect with the discarding holes DP′a and DP′a, but it is not necessary to drill them, and the discharge ports DP and DP are eliminated. Can be resized in the vicinity of the position communicating with the discharge oil passages DR, DR, the number of processing steps can be reduced, and the cost can be reduced.
[0017]
  And, since the perforation angle of the discharge port DP / DP is set to θ (<180 °) with respect to the suction port SP in this way, it is covered with a small bonnet 4 as shown in FIG. Even in this case, the discharge pipes DT and DT connected to the discharge ports DP and DP can be piped without interfering with the bonnet 4.
[0018]
  In addition to this, for example, as shown in FIG. 17, the discharge ports DP and DP are formed in the front end surface of the hydraulic pump P in the same direction as the pump shaft PS, or as shown in FIG. The thing etc. which perforated discharge port DP * DP on the same side as SP are considered. In any case, since the interference part of the bonnet 4 is reduced, the bonnet 4 is reduced in size, contributing to compactness and improved turning performance.
[0019]
  Thus, in the turning work vehicle in which the main body portion 3 has a substantially circular shape in plan view, the outer periphery of the main body portion 3 is located inside the outer edge portions of the left and right crawler portions 10a and 10a as shown in FIG. In other words, the turning radius is less than half of the vehicle width between the left and right crawler parts 10a and 10a, and the main body part 3 does not protrude outside the crawler part 10a during turning and can be turned slightly. It becomes a simple structure.
[0020]
  Various hydraulic valves are provided in the front column 6 as shown in FIG. Among these, the dual-function pedal 1 pivotally supported so as to be pivotable in the left and right substantially center line portion is disposed on the left foot portion as viewed from the seat 5 with respect to the front column 6. Via the pivot shaft 1c, the left side portion, that is, the outer side of the main body portion 3 is used as a speed increasing drive pedal portion 1a, and the right side portion, that is, the inner side of the main body portion 3 is set as a PTO driving pedal portion. 1b. In constructing such a swivel work vehicle, a model in which various functions can be operated has a limited space for the operation tool. In Japanese Patent Application No. 7-172456, which has already been filed, the present applicant has disclosed a dual-function pedal having both a speed increasing drive pedal portion and a PTO driving pedal portion.
[0021]
  The structure of the dual function pedal will be described with reference to FIGS. FIG. 19 is a side view of a conventional dual-function pedal 1 ″, FIG. 20 is a plan view when the pedal cover 2 ′ is covered, FIG. 21 is a plan view when the pedal cover 2 ′ is opened, and FIG. It is a front view at the time of opening of cover 2 '.
[0022]
  First, the dual function pedal 1 "is pivotally supported by the pedal step plate 3b on the side of the front column 6 of the turning type work vehicle so as to be able to turn left and right. The speed increasing drive pedal portion 1 ″ a is located on the left side when viewed from the seat, that is, the outer side of the main body 3 via the dynamic shaft 1 ″ c, and the PTO drive pedal portion 1 is located on the right side, ie, the inward side. "B" is formed. In the vicinity of the PTO driving pedal portion 1'b, a stopper 11 'is pivotally supported on the pedal portion step plate 3b so as to be horizontally rotatable, and the PTO driving pedal portion 1 is formed. In the state where 'b is in the upward rotation position, if it is desired to be in the non-operating state, the pedal is pivoted to the lower position of the PTO driving pedal portion 1'b to regulate the stepping allowance.
[0023]
  In addition, the dual function pedal 1 "is covered with a cover on the upper part in order to prevent erroneous operation and to secure a stepping foot during excavation work. That is, in front of the dual function pedal 1". The pedal cover 2 'is pivotally supported by a pivot shaft 2'a so as to be pivotable back and forth. When the pedal is not required, the pedal cover 2 is brought into the state A in FIG. 19 and the state in FIG. 'Is put on the dual function pedal 1 "and when the pedal is depressed, the pedal cover 2' is opened by rotating forward as shown in the state B of FIG. 19, FIG. 21 and FIG. It is.
[0024]
  First, a description will be given of a problem with a dual function pedal for speed-up and PTO driving. Of the dual-function pedal 1 ", the PTO drive pedal 1" b is not necessary unless a PTO transmission working machine is attached, but the speed-up drive pedal 1 "a is frequently used. However, as described above, in the structure of the pedal cover 2 'that is pivotable back and forth, the operation of opening the pedal drive pedal 1'a so that the pedal can be stepped on every time it is used. Is necessary and complicated. Accordingly, it is desirable to allow the vehicle to be stepped on when necessary even with the cover applied, but on the other hand, it is required to devise a device that does not step in unnecessarily.
[0025]
  Further, the PTO driving pedal portion 1 ″ b is located closer to the inside and near the foot of the front column 6, and therefore, it is difficult to step on the pedal when the pedal position is low. When 'is applied, there is a limitation that interference with the feet is avoided and it is not possible to step in unnecessarily.
[0026]
  A pedal cover 2 is pivotally supported on the front part of the dual-function pedal 1 so as to be able to turn back and forth by a turning shaft 2a, as described in the prior art. 3 and the state shown in FIG. 5 is released, the entire dual-function pedal 1 is released, and both the speed increasing drive pedal portion 1a and the PTO driving pedal portion 1b are depressed. Is possible. In this state, the stepping height of the PTO driving pedal portion 1b is at a low position in the conventional one, and the stepping amount cannot be taken sufficiently and the stepping operation is difficult. However, in the present embodiment shown in FIGS. The PTO driving pedal portion 1b is set to a certain level so that it can be easily stepped on and a large step allowance can be taken. However, the height is limited. This will be described later.
[0027]
  In the state A in FIG. 3 and the state in which the pedal cover 2 is rotated backward to cover the dual function pedal 1 as shown in FIG. 4, conventionally, the speed increasing drive pedal portion 1 a is also completely covered. However, the speed increasing drive pedal portion 1a protrudes more outward than the pedal cover 2 in a covered state in consideration of the fact that it is used frequently during work. Further, as shown in FIG. 4, the main body 3 is extended outward. As a result, even when the pedal cover 2 is covered, it is possible to move the foot slightly outward and depress the speed increasing drive pedal portion 1a. Further, the normal foot position during the work is the upper part of the pedal cover 2 that has been covered, so that the foot placed here does not interfere with the speed increasing drive pedal portion 1a, and therefore an erroneous operation is caused. It can be avoided. In order to stabilize the position of the foot when hung on the speed increasing drive pedal portion 1a at the outer position, the speed increasing drive pedal portion 1a bends the outer end upward in an L shape. ing.
[0028]
  Further, although the stepping height of the PTO driving pedal portion 1b is increased as described above, it is unnecessary if the PTO driving pedal portion 1b can be stepped in the state where the pedal cover 2 is covered. The PTO shaft will be driven, and this will be an obstacle to foot operation in addition to power loss. Therefore, the depression height of the PTO driving pedal portion 1b is set to the same height as the pedal cover 2 as shown in FIG. 3 in the neutral state where the acceleration driving pedal portion 1a is not depressed. Further, as shown in FIG. 4, a stopper 11 is pivotally supported on the pedal unit step plate 3b in the vicinity of the PTO driving pedal unit 1b so as to be horizontally rotatable. The stepping amount of the PTO driving pedal portion 1b is guaranteed, but when not operated (when the pedal cover 2 is covered), as shown by the broken line portion, the pedal is rotated to a position below the PTO driving pedal portion 1b. Even if the foot to be placed on the pedal cover 2 is applied to the PTO driving pedal portion 1b, there is no stepping allowance.
[0029]
  However, on the other hand, in order to be able to step on the speed increasing pedal unit 1a even when the pedal cover 2 is covered, the PTO driving pedal unit 1b must be able to move above this position. I must. Therefore, a notch portion 2b is formed at the position where the pedal portion 1b for driving the PTO in the pedal cover 2 is disposed, and the pedal portion 1b for driving the PTO from the pedal cover 2 in the notch portion 2b. It can also be turned higher. The height of the PTO driving pedal portion 1b is higher than that of the pedal cover 2 only when the foot is placed on the acceleration driving pedal portion 1a. There is no worry that the feet on the driving pedal portion 1b interfere with each other.
[0030]
  The dual function pedal 1 'shown in FIGS. 6 to 11 will be described. The speed increasing drive pedal 1'a has the same configuration as that of the speed increasing driving pedal 1a of the dual function pedal 1 shown in FIGS. 3 to 5 and protrudes outward even when the pedal cover is covered. It is extended as possible. The pedal cover has the same structure as the pedal cover 2 'in the prior art, that is, the pedal cover 2 is not formed with a notch 2b. Is completely covered and cannot be stepped on.
[0031]
  In such a configuration in which the pedal cover 2 is provided, the PTO driving pedal portion 1′b is separated from the dual function pedal 1 ′ in order to increase the stepping position of the PTO driving pedal portion. 11 is pivotally supported by the dual function pedal 1 'so as to be pivotable up and down, and is fixed at a position pivoted downward when the pedal cover 2 is applied, and is pivoted upward when necessary. It is fixed so that the stepping height can be increased.
[0032]
  The assembly structure of the PTO driving pedal portion 1'b with respect to the dual function pedal 1 'will be described with reference to FIGS. The head portion of the bolt 12 serving as a pivot shaft is welded and fixed to the end portion of the dual function pedal 1 'so that the screw portion protrudes to the right side when viewed from the seat 5 and to the inward side with respect to the main body portion 3. Yes. As shown in FIG. 10, a washer 13, a PTO driving pedal portion 1'b, a disc spring 14, 14 and a washer 13 are fitted into the threaded portion, and a nut 15 is fitted from the outer end portion, thereby the PTO driving pedal portion. 1′b is fixed. When the nut 15 is loosened, the PTO driving pedal portion 1'b can turn freely (the turning resistance force acts to some extent by the disc springs 14 and 14), and when the PTO is not operated as shown in FIG. It is rotated to the position of the solid line (when covered by the pedal cover 2) and to the position of the dotted line at the time of operation, the nut 15 is tightened, and the PTO driving pedal portion 1'b is fixed at each position. In the vicinity of the PTO driving pedal portion 1'b, a stopper 11 'is pivotally supported on the pedal portion step plate 3b so as to be horizontally rotatable, and the PTO driving pedal portion 1'b is set to an upward rotation position. In the state, if it is desired to be in a non-operating state, it is rotated to a position below the PTO driving pedal portion 1'b to regulate the stepping allowance.
[0033]
  Since it comprised as mentioned above, first, in the dual function combined pedal comprised so that the operation tool in a turning type work vehicle might be compactized, since it comprised like Claim 1, the speed-up drive pedal part with a high use frequency is comprised. It can be stepped on when the pedal cover is applied, and it protrudes to the outside of the main body, so that the pedal for the acceleration drive pedal is inadvertent during normal work with the foot on the pedal cover. There is no such thing as interference and misoperation.
[0034]
  Similarly, since the dual function pedal is configured as described in claim 2, since the stepping position of the PTO driving pedal portion is increased, the stepping allowance can be taken and the stepping operation is facilitated. Even in this case, the PTO shaft is not unnecessarily driven by making it impossible to depress the pedal when it is covered with the pedal cover.
[0035]
  Similarly, since the variable displacement hydraulic piston pump is configured as described in claim 4, the drilling angle of the discharge port with respect to the suction port is not limited to an arbitrary, that is, 180 °, so that the bonnet and the discharge port can be provided. The part that interferes with the pressure oil discharge pipe to be connected can be eliminated, and the bonnet is made smaller by that amount, which also contributes to improving the turning performance.
[0036]
【The invention's effect】
  Since the present invention is configured as described above, the following effects can be obtained.
  Since the variable displacement hydraulic piston pump directly connected to the engine installed in the bonnet is constructed as described in claim 1, the lateral width from the engine built in the hood to the tip of the pump can be further reduced. The width of itself can be shortened, which contributes to further improvement in turning performance.
[0037]
  Further, regarding the variable displacement hydraulic piston pump directly connected to the engine, by configuring as in the present invention, the bonnet can be miniaturized and a turning work vehicle with higher turning performance can be provided.
  As a result, particularly in a swivel excavator having a turning radius of approximately one-half of the vehicle width and a turning frame having a substantially circular shape, the operability of each pedal portion is high, and the bonnet is downsized. There is. Further, the present invention can be applied to a swing work vehicle, for example, a swing crane vehicle, a swing excavator, and a swing crusher.
[Brief description of the drawings]
FIG. 1 is an overall side view of a turning work vehicle.
FIG. 2 is a plan view of the main body 3 showing the internal configuration of the bonnet 4;
FIG. 3 is a side view of the dual function pedal 1;
FIG. 4 is a plan view of the pedal cover 2 when covered.
FIG. 5 is a front view when the pedal cover 2 is opened.
FIG. 6 is a side view of the dual function pedal 1 ′.
FIG. 7 is a plan view when the pedal cover 2 ′ is covered.
FIG. 8 is a plan view when the pedal cover 2 ′ is opened.
FIG. 9 is a front view of the pedal cover 2 'when it is opened.
FIG. 10 is a partial plan view showing an assembled configuration of a PTO driving pedal portion 1 ′ b in the dual function pedal 1 ′.
FIG. 11 is a partial side view showing a rotational configuration of a PTO driving pedal portion 1 ′ b in the dual function pedal 1 ′.
FIG. 12 is a front view showing a direct connection configuration of a hydraulic pump P with respect to a flywheel housing FWH.
13 is a side view showing the piping direction of the suction oil pipe and the discharge oil pipe with respect to the hydraulic pump P. FIG.
14 is a schematic side view of the main body 3 showing the piping direction in the bonnet 4 as well. FIG.
15A and 15B are views showing a suction / discharge port housing PH attached to the hydraulic pump P, where FIG. 15A is a side view and FIG. 15B is a front view.
FIG. 16 is a cross-sectional view taken along line XX in FIG.
FIG. 17 is a perspective view of a hydraulic pump P to which a suction discharge port housing PH having a discharge port DP formed in the pump axial direction is attached.
18 is a schematic side view of the main body 3 showing the piping direction in the bonnet 4 when a hydraulic pump P assembled with a suction / discharge port housing PH having a discharge port DP formed on the same side as the suction port SP is used. It is.
FIG. 19 is a side view of a conventional dual-function pedal 1 ″.
FIG. 20 is a plan view when the same is covered with a pedal cover 2 ′.
FIG. 21 is a plan view when the pedal cover 2 ′ is opened.
FIG. 22 is a front view of the pedal cover 2 'when it is opened.
FIG. 23 is a front partial sectional view showing a direct connection structure between a conventional hydraulic pump P and a flywheel housing FWH.
FIG. 24 is a partial front sectional view showing a direct connection structure between another conventional hydraulic pump P and a flywheel housing FWH.
FIG. 25 is a side view showing a piping direction of a suction / discharge oil pipe in a conventional hydraulic pump P.
26 is a schematic side view of the main body 3 showing the piping direction of the suction / discharge oil pipes in the bonnet 4 as well. FIG.
27A and 27B are views showing a conventional suction / discharge port housing PH ', where FIG. 27A is a side view and FIG. 27B is a front view.
FIG. 28 is a cross-sectional view taken along line X′-X ′ in FIG.
[Explanation of symbols]
  1.1 'Dual-function pedal
  1a / 1'a Speed-up drive pedal
  1b · 1'b PTO drive pedal
  2.2 'Pedal cover
  2a Notch
  3 Body
  4 Bonnet
  5 seats
  6 Front column
  P Hydraulic pump
  PS pump shaft
  C Coupling part
  Ca recess
  PM pump mount
  PH Suction / discharge port housing
  SP suction port
  DP discharge port
  DR Discharge oil passage
  ST Suction oil pipe
  DT discharge oil pipe
  FWH flywheel housing
  FW Flywheel
  Fwa insertion hole
  10a Crawler part

Claims (2)

In the configuration in which the pump shaft PS of the variable displacement hydraulic piston pump P is directly connected to the flywheel FW of the engine E mounted on the main body of the turning work vehicle, the projecting portion protrudes from the variable displacement hydraulic piston pump P. A coupling part C is attached and engaged to the tip of the pump shaft PS, the coupling part C is fitted in the insertion hole FWa of the flywheel FW, and the coupling part C and the flywheel FW are connected by the fastening bolt 16. A swiveling work vehicle configured to be fixed and having the coupling portion C of the pump shaft PS completely fitted in the insertion hole FWa of the flywheel FW . 2. The turning work vehicle according to claim 1, wherein the shape of the pump mount PM for engaging and fixing the variable displacement hydraulic piston pump P to the flywheel housing FWH is fixed to the central portion of the fixed displacement hydraulic piston pump P. When approaching the flywheel FW side and the fixed side of the outer peripheral portion of the flywheel housing FWH with the variable displacement hydraulic piston pump P side, when viewed from the hydraulic pump P side, the central portion of the pump mount PM is A swivel work vehicle characterized by a concave configuration .

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