WO2014118876A1 - 回転型流体機械 - Google Patents
回転型流体機械 Download PDFInfo
- Publication number
- WO2014118876A1 WO2014118876A1 PCT/JP2013/051844 JP2013051844W WO2014118876A1 WO 2014118876 A1 WO2014118876 A1 WO 2014118876A1 JP 2013051844 W JP2013051844 W JP 2013051844W WO 2014118876 A1 WO2014118876 A1 WO 2014118876A1
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- WO
- WIPO (PCT)
- Prior art keywords
- side plate
- seal member
- gear
- seal
- fluid machine
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
- F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
- F04C15/0007—Radial sealings for working fluid
- F04C15/0019—Radial sealing elements specially adapted for intermeshing-engagement type machines or pumps, e.g. gear machines or pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/10—Outer members for co-operation with rotary pistons; Casings
- F01C21/104—Stators; Members defining the outer boundaries of the working chamber
- F01C21/108—Stators; Members defining the outer boundaries of the working chamber with an axial surface, e.g. side plates
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
- F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
- F04C15/0023—Axial sealings for working fluid
- F04C15/0026—Elements specially adapted for sealing of the lateral faces of intermeshing-engagement type machines or pumps, e.g. gear machines or pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
- F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
- F04C15/0034—Sealing arrangements in rotary-piston machines or pumps for other than the working fluid, i.e. the sealing arrangements are not between working chambers of the machine
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
- F04C2/14—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
- F04C2/18—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with similar tooth forms
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C19/00—Sealing arrangements in rotary-piston machines or engines
- F01C19/005—Structure and composition of sealing elements such as sealing strips, sealing rings and the like; Coating of these elements
Definitions
- the present invention relates to a rotary fluid machine using gears such as a gear pump or a gear motor.
- a gear pump is used as a hydraulic pressure source of an actuator used for a moving body such as a construction machine, a robot, and an automobile (see, for example, Japanese Patent Laid-Open No. 10-252589 (Patent Document 1)).
- the pressure compartment seal When the pressure compartment seal is installed at a predetermined position such as a groove or a step, the dimensional tolerance of each part is taken into account, and when assembled, there is a crushing allowance of the pressure compartment seal and the contact surface pressure with the side plate or gear case It must be designed with the dimensions to contact with. In other words, in order to reliably close the gap formed between the side plate or seal block and the gear case, the height of the groove formed in the side plate or seal block is designed to be lower than the height of the pressure compartment seal. . As a result, after the gear pump is assembled, the pressure compartment seal is crushed and is brought into close contact with the side plate or seal block while generating a contact surface pressure.
- the gear pump is a section where two gears mesh with each other, and there is a region where the gears come into contact with each other at two locations at a certain rotation angle and are closed between the tooth spaces of the two gears.
- the volume of the confinement region changes with the rotation of the gear, but since the volume is small, the pressure fluctuation increases even with a minute volume change. Therefore, the side plate provided so as to sandwich the two gears is peeled off from the side surface of the gear by the force generated by this pressure fluctuation, and the high pressure region (discharge port side) and the low pressure region (suction port side) in the pump May reduce the volumetric efficiency of the pump.
- Patent Document 1 since the cross section of the pressure compartment seal is formed in a stepped shape, the thickness of the cross section of the portion to be crushed becomes thin, and as a result, the amount crushed between the side plate or seal block and the gear case is sufficient. As a result, the force that pushes the side plate that generates the pressure compartment seal in the gear direction after the pump is assembled is reduced, and it is possible to avoid an increase in load torque due to increased friction between the side plate and the gear. .
- the pressure compartment seal has a uniform cross-sectional shape over the entire length of the seal.
- Patent Document 1 in the case of a gear pump that seals the tip of a tooth with a seal block in a relatively short section, the region of high pressure varies depending on the rotation angle of the gear. When the high pressure region enters the position closest to the suction port (low pressure region), the force for peeling the side plate from the gear side surface is maximized.
- Patent Document 1 since the cross-sectional shape of the pressure compartment seal is uniformly formed over the entire length of the seal, a force that pushes the side plate toward the gear side by forming the cross-sectional shape stepwise. Is reduced, it cannot resist the force to peel the side plate from the side surface of the gear.
- a gap may be formed between the side plate and the gear in the assembled state due to the side plate warpage and surface accuracy.
- the side plate When the side plate is made of a low-rigidity material such as resin, the side plate can be deformed and brought into close contact with the gear by the force generated by the pressure compartment seal, but when a pressure compartment seal with a uniform cross-sectional shape is used In places where there is no gap, a force that pushes the side plate toward the side of the gear is generated more than necessary, and friction increases.
- the conventional pressure compartment seal reduces leakage inside the pump based on pressure fluctuations acting locally, and further, between the side plate or seal block and the gear. It is difficult to realize an improvement in pressure response and a reduction in driving torque by suppressing the increase in friction. This problem also occurs in the gear motor.
- An object of the present invention is to provide a rotary fluid machine capable of realizing a reduction in leakage inside a gear pump or a gear motor and an improvement in responsiveness.
- the force of the seal member which forms a pressure compartment installed between the side plate and the case, pushes the side plate toward the gear side is not made uniform over the entire length of the seal member, but partially strengthened. It is a thing.
- FIG. 1 is a cross-sectional view showing a basic configuration of a first embodiment of a gear pump according to the present invention, which is a cross-sectional view in a direction perpendicular to a drive shaft.
- FIG. 2 is an AA cross-sectional view of the gear pump shown in FIG. 1.
- FIG. 2 is a cross-sectional view of the gear pump shown in FIG. 1 taken along the line BB.
- It is the F section enlarged view of the gear pump shown in FIG. 2, Comprising: The figure which shows the state after the pump assembly completion of the sealing member applied with the gear pump of Example 1.
- FIG. It is the G section enlarged view of the gear pump shown in FIG.
- FIG. 6 is an enlarged view of a G portion of the gear pump shown in FIG. 5, and shows a state after a pump assembly of a seal member having a cross-sectional shape different from that of FIG. 7 applied in the gear pump of the first embodiment. It is the G section enlarged view of the gear pump shown in FIG. 5, Comprising: The figure which shows the state before and behind the pump assembly of the sealing member which has a cross-sectional shape different from FIG. 7 applied with the gear pump of Example 1.
- FIG. 6 is an enlarged view of a G part in FIG.
- FIG. 5 when the seal member shown in the second embodiment is applied to the gear pump according to the present invention, and shows the state before and after the pump assembly of the seal member.
- FIG. 3 is an enlarged view of a portion F in FIG. 2 when the seal member shown in the second embodiment is applied to the gear pump according to the present invention, and shows the state before and after the pump assembly of the seal member.
- FIG. 6 is an enlarged view of a G part in FIG. 5 when the seal member shown in the third embodiment is applied to the gear pump according to the present invention, and shows the state before and after the pump assembly of the seal member.
- FIG. 5 is an enlarged view of a portion F in FIG.
- FIG. 17 is an HH sectional view of the gear pump shown in FIG. 16. Schematic which shows the arm which operate
- FIG. 1 is a view showing a basic configuration of a gear pump 1 having a seal member according to Embodiment 1 of the present invention, and is a cross-sectional view in a direction perpendicular to the drive shaft.
- 2 is a sectional view taken along line AA of the gear pump shown in FIG. 1
- FIG. 3 is a sectional view taken along line EE of the gear pump shown in FIG. 2
- FIG. 4 is a sectional view taken along line BB of the gear pump shown in FIG.
- It is CC sectional drawing of the gear pump shown in FIG. 1 corresponds to a DD cross-sectional view of the gear pump shown in FIG.
- the gear pump 1 includes a pump assembly 10.
- the pump assembly 10 includes a drive shaft (drive shaft) 2, a driven shaft (driven shaft) 3, a pair of gears 4, 4 ′, a drive pin 5, a pair of side plates 6, 6 ′, and a seal block 7. With.
- the drive shaft 2 is connected to a drive source (not shown) such as an external electric motor and is driven to rotate.
- the driven shaft 3 is rotated by a rotational force applied from the drive shaft 2 via a pair of gears 4 and 4 ′.
- the pair of gears 4 and 4 ′ are respectively supported by the drive shaft 2 and the driven shaft 3, and the tooth tips mesh with each other.
- the drive pin 5 is inserted into both the shafts 2 and 3 so that the drive shaft 2, the driven shaft 3 and the gears 4 and 4 'rotate together.
- the pair of side plates 6 and 6 ′ are disposed adjacent to both side surfaces of the gears 4 and 4 ′, and contact the seal block 7 as shown in FIGS.
- the seal block 7 is in contact with the side plates 6 and 6 ′ at the contact surface 21, and covers a part of the circumferential direction of the gears 4 and 4 ′ as shown in FIG. It is arranged opposite the tooth tip in the vicinity of the suction port). That is, the seal block 7 is close to the tooth tips of the gears 4 and 4 ′ within a certain range in the circumferential direction of the gears 4 and 4 ′.
- the side plate 6 is disposed adjacent to the side surface 4b of the gear 4 and the side surface 4b ′ of the gear 4 ′, and the side plate 6 ′ is disposed on the side surface 4a of the gear 4 and the side surface 4a of the gear 4 ′. It is placed adjacent to '.
- the side surfaces 4b, 4b 'of the gears 4, 4' are slidably contacted with the side plate 6, and the side surfaces 4a, 4a 'of the gears 4, 4' are slidably contacted with the side plate 6 '.
- the side plates 6 and 6 ′ seal both side surfaces of the gears 4 and 4 ′.
- the side plates 6 and 6 ′ are formed in the same shape so that parts can be shared, and have a suction port 19 serving as a suction hole as shown in FIG. 1.
- the shape of the outer edge of the side plates 6, 6 ′ in the vicinity of the suction port 19 is an arc shape substantially equal to the outer diameter of the circle formed by the tooth tips of the gears 4, 4 ′.
- the contact surface of the seal block 7 with the side plates 6 and 6 ' has substantially the same shape as the arc-shaped portion of the side plates 6 and 6'.
- the seal block 7 and the side plates 6, 6 ' are in close contact with each other at the contact surface 21 of the side plates 6, 6'.
- the pump assembly 10 is accommodated in a case 13 including a front case 11 and a rear case 12 as shown in FIG.
- the front case 11 and the rear case 12 are composed of members different from the seal block 7.
- the rear case 12 has a recess 12a.
- a space for sealing the liquid is formed by attaching the front case 11 to the open end of the recess 12 a.
- the pump assembly 10 includes seal members 8, 6 a, 6 a ′ on the side plates on both ends in the extending direction of the drive shaft 2 and steps 7 b, 7 b ′ on the seal block.
- 8 ' is installed and supported by being sandwiched between the front case 11 and the rear case 12 via the seal members 8, 8'.
- the front case 11 and the rear case 12 are aligned with each other by a knock pin 9 shown in FIG.
- the steps 6 a and 6 a ′ and the steps 7 b and 7 b ′ are notches formed in the outer peripheral portion of the side plates 6 and 6 ′ and the inner peripheral portion of the seal block 7.
- the steps 6a and 6a ′ and the steps 7b and 7b ′ are formed as the notches, but instead of the steps, grooves are formed in the side plates and the seal blocks, and the seal members 8 and 8 ′ are formed in the grooves. You may make it install.
- the seal members 8 and 8 ' are formed of an elastic body such as rubber.
- the recess 12a of the rear case 12 has, for example, the shape shown in FIGS. 1 and 3, and accommodates the pump assembly 10 and the seal members 8 and 8 'as shown in FIGS.
- the surface 12b of the recess 12a of the rear case 12 facing the seal block 7 forms a part of a cylindrical surface (a cylindrical inner peripheral surface extending in the extending direction of the drive shaft).
- a surface 7a of the seal block 7 facing the recess 12a of the rear case 12 also forms a part of a cylindrical surface (an outer peripheral surface of a cylinder extending in the extending direction of the drive shaft). Therefore, the pump assembly 10 is constrained to be rotatable around the rotation axis, with a straight line passing through the center of the arc of the opposing surface 12b of the rear case recess being a cylindrical surface and parallel to the drive shaft 2 as a rotation axis.
- the recess 12a of the rear case 12 is provided with a protruding portion 12c at one location on the inner wall.
- the protrusion 12 c is connected to the rotation shaft of the pump assembly 10 with respect to the drive shaft 2 in the direction connecting the drive shaft 2 and the driven shaft 3 (left and right direction in FIGS. 1 and 3). Is provided on the opposite side, that is, on the left and below the drive shaft 2.
- the position where the protrusion 12c shown in FIGS. 1 and 3 is provided is an example, and the present invention is not limited to this.
- the protruding portion 12c contacts one of the two side plates 6, 6 ′ (the side plate 6 ′ far from the front case 11 in FIG. 4), and the pump assembly 10 has been described above. Suppresses rotation around the rotation axis.
- the side plate 6 ′ is opposite to the rotational axis of the pump assembly 10 with respect to the drive shaft 2 in the direction connecting the drive shaft 2 and the driven shaft 3 (the left-right direction in FIGS. 1 and 3).
- the portion on the side comes into contact with the protruding portion 12 c provided in the recess 12 a of the rear case 12.
- urging mechanisms 14a and 14b are provided to press the side plates 6 and 6 'in the direction in which the seal block 7 is located.
- the urging mechanisms 14a and 14b are elastic bodies, and are composed of, for example, a spring and a pin. As shown in FIGS. 1, 3, and 5, the urging mechanisms 14a and 14b are disposed between the side plates 6 and 6 'and the inner wall of the rear case recess 12a.
- the urging mechanism 14a is arranged to rotate the pump assembly 10 in the same direction as the rotation direction R1 of the drive shaft 2 and the gear 4, and presses the side plate 6 '. That is, the urging mechanism 14a is located at the position of the protrusion 12c (left side in FIG. 3) with respect to the rotation axis of the pump assembly 10 in the direction connecting the drive shaft 2 and the driven shaft 3 (left and right direction in FIG. 3). It is arrange
- the urging mechanism 14 b is configured so that the pump assembly 10 can move in a direction (vertical direction in FIG. 3) perpendicular to the direction connecting the drive shaft 2 and the driven shaft 3 and the extending direction of the drive shaft 2. It arrange
- the pump assembly 10 is housed in the recess 12a of the rear case 12 so as to be rotatable around the rotation axis.
- the rotation of the pump assembly 10 is suppressed by the urging mechanism 14 a pressing the side plate 6 ′ against the protrusion 12 c of the recess 12 a of the rear case 12.
- the position of the pump assembly 10 within the recess 12a of the rear case 12 is determined.
- the position of the side plate 6 is fixed in a state where the side plate 6 is not in contact with the concave portion 12 a of the rear case 12 but is pressed by the urging mechanism 14 b and is in close contact with the seal block 7 at the contact surface 21.
- one side plate 6 ′ plays a role of fixing the position of the pump assembly 10, and the other side plate 6 contacts the seal block 7 held on the facing surface 12 b of the recess 12 a of the rear case 12. It is fixed by doing. Therefore, even when the shape of the contact surface 21 with the seal block 7 is slightly different between the two side plates 6 and 6 ′ due to processing errors, one side plate is in close contact with the other side plate and the seal block 7. Will not be disturbed.
- the front case 11 has a groove 15 on a contact surface with the rear case 12.
- a case seal 16 is disposed in the groove 15. The case seal 16 seals a gap that may be generated between the front case 11 and the rear case 12 to prevent the liquid in the rear case 12 from leaking to the outside.
- the front case 11 is provided with a recess 17 on the surface opposite to the contact surface with the rear case 12 (for example, the lower surface in FIG. 2).
- An oil seal 18 is disposed in the recess 17.
- the oil seal 18 is press-fitted into the concave portion 17 of the front case 11, the outer peripheral surface is in close contact with the wall surface of the concave portion 17, and the outer peripheral surface of the drive shaft 2 is slidably in contact with the inner peripheral surface.
- the oil seal 18 seals a gap formed between the drive shaft 2 and the front case 11 so that the liquid in the pump chamber does not leak to the outside when the gear pump is driven.
- the suction port 19 is formed by the side plates 6, 6 ′, the seal block 7, and the rear case 12. Further, the discharge port 20 is formed by the flow path formed in the rear case 12. The discharge port 20 communicates with the recess 12a of the rear case 12 as shown in FIGS.
- a tank (not shown) for supplying liquid to the gear pump 1 is connected upstream of the suction port 19.
- a valve, a cylinder (not shown) or the like is connected downstream of the discharge port 20 to adjust the pump discharge pressure.
- the drive shaft 2 is connected to a drive source (not shown) such as a motor.
- the gear pump 1 When the gear pump 1 is driven, a high pressure region and a low pressure region are formed in the recess 12a of the rear case 12. The high pressure region and the low pressure region are partitioned by each component described below. The seal by each of these parts will be described.
- the gear pump 1 includes a meshing portion of the gears 4 and 4 ′, a proximity surface between the tooth tips of the gears 4 and 4 ′ and the seal block 7, side surfaces 4 a, 4 b, 4 a ′ and 4 b ′ and side plates 6 of the gears 4 and 4 ′.
- the seal members 8 and 8 ′ partition the liquid so that the liquid does not communicate when a differential pressure is generated between the periphery of the suction port 19 and the periphery of the discharge port 20.
- the inside of the seal members 8, 8 ' is a low pressure region, and the outside is a high pressure region.
- the seal members 8, 8 'used in this embodiment will be described. Since the seal members 8 and 8 ′ are brought into close contact with the inner surfaces of the side plates 6 and 6 ′ and the case 13 (the front case 11 or the rear case 12) when the gear pump 1 is assembled, the side plates 6a and 6a ′ and the front case 11 or The height of the seal members 8 and 8 'is made larger than the gap with the rear case 12 (vertical direction in FIG. 2). Thus, after assembling the gear pump 1, the seal members 8 and 8 ′ are crushed in the direction of the drive shaft and are in close contact with the side plates 6 and 6 ′, the front case 11, and the rear case 12 while generating contact surface pressure.
- the portion 81 passing through the position corresponding to the portion with which the gears 4 and 4 ′ mesh, the side plates 6 and 6 ′, and the seal block 7 are in contact with each other.
- the cross-sectional shape of the portion 82 that is closer to the gear rotation center than the section where the sealing is performed and passes through the position where the liquid in the suction port 19 is sent to the high pressure region is the other portion (the portion 83 or the portion 84 having no or little pressure fluctuation).
- the positions corresponding to the meshing portions of the gears 4 and 4 ′ are not only the portions that are actually meshing as shown in FIG. 1, but the gear tips of the gears 4 and 4 ′ gradually become closer with rotation.
- the width of the seal member 8 may be widened in the region. Further, the portion 82 of the seal member 8 is located at the position near the gear rotation center from the contact portion between the seal block 7 and the side plates 6 and 6 'as shown in the wide portion of the seal member 8 in FIG. The width may be increased by a certain length in the direction.
- the portion 83 or 84 of the seal member 8 has an L-shaped cross section, for example.
- a portion 85 for reducing the thickness of the sealing member is provided to reduce the force of pushing the side plate 6 generated by the sealing member 8 to the gears 4 and 4 ′ when crushed.
- the portion where the width of the seal member is reduced is formed on the side plate 6 side, and the portion 86 where the thickness is increased is formed on the front case 11 side, but the portion where the width of the seal member is increased is formed on the side plate 6 side.
- the formed and thinned portion 86 may be formed on the front case 11 side.
- the seal member 8 has a level difference in the portions 81 and 82 of the seal member 8. It is set as the structure extended on the outer side (downward of FIG. 7) of 6a. As a result, this portion 81 has a greater force to push the side plate 6 in the direction of the gears 4 and 4 ′ than the portion 83 and the portion 84.
- the force by which the sealing member in the position (region) corresponding to the portion where the pressure fluctuation is large pushes the side plate 6 in the direction of the gears 4, 4 ′ is the other portion (the portion where there is no or little pressure fluctuation).
- This is realized by partially changing the width of the seal member.
- the width of the seal member is changed from the portion 81 to the portion 84 so that the width gradually decreases.
- the present invention is not limited to this. Absent.
- the drive shaft 2 is driven by a drive source (not shown) such as a motor as described above.
- the gear 4 is supported so as to rotate integrally with the drive shaft 2. For this reason, when the drive shaft 2 rotates in the rotation direction R1 shown in FIG. 3, the gear 4 also rotates in the rotation direction R1.
- the gear 4 ′ meshes with the gear 4 and the tooth tips, and rotates together with the driven shaft 3. For this reason, when the gear 4 rotates in the rotation direction R1, the gear 4 'rotates together with the driven shaft 3 in the rotation direction R2.
- Rotating the gears 4 and 4 ′ disengaging the teeth increases the volume of the space around the suction port 19, and as a result, liquid is sucked from the suction port 19.
- the liquid around the suction port 19 is accommodated in the tooth spaces of the gears 4 and 4 ′ by the rotation of the gears 4 and 4 ′ and conveyed along the rotation directions R ⁇ b> 1 and R ⁇ b> 2 of the gears 4 and 4 ′.
- the conveyed liquid flows out of the tooth space as the gears 4 and 4 'rotate.
- liquid does not communicate between the periphery of the suction port 19 and the periphery of the discharge port 20 of the gear pump 1 by the seal of each component. For this reason, the pressure rises around the discharge port 20 due to the liquid flowing out of the tooth gap, and the liquid is discharged from the discharge port 20.
- the gear pump 1 has a low pressure only inside the seal members 8 and 8 ', and the other portions have a high pressure.
- the gears 4 and 4 ' may be in contact with each other at two points depending on the rotation angle.
- an area (closed area) surrounded by the tooth gaps of the two gears 4 and 4 ′ and the side plates 6 and 6 ′ is formed, and the volume is reduced by the rotation of the gears 4 and 4 ′, and then increased.
- the volume of the confinement region is small, a large pressure change is caused by a minute volume change, and the side plates 6 and 6 ′ receiving this pressure are peeled from the side surfaces of the gears 4 and 4 ′ (see FIG. 2). Receives great force in the vertical direction.
- the place where the pressure change occurs at the meshing portion is at a position shifted from the center of gravity of the side plate, and the seal member 8 is asymmetric with respect to a straight line passing through the centers of the drive shaft 2 and the driven shaft 3 as shown in FIG. With contours. Therefore, when the seal member 8 has the same cross-sectional shape as a whole and is configured to push the side plates 6 and 6 ′ in the direction of the gears 4 and 4 ′ with a light force, the side plates 6 and 6 ′ are caused by the pressure at the meshing portion. There is a possibility that the volume efficiency is lowered because the low pressure region and the high pressure region of the gear pump 1 are communicated with each other while the gear pump 4 is separated from the side surfaces of the gears 4 and 4 ′.
- the tooth tips of the gears 4 and 4 ′ are partially sealed by the seal block 7.
- the seal block 7 depending on the angle of the gears 4 and 4 ′, as shown in FIG. Liquid enters. Also in this case, the side plates 6 and 6 'receive a force in the direction of being peeled off from the side surfaces of the gears 4 and 4', and the side plates 6 and 6 ' There is a possibility that a high-pressure region and a low-pressure region communicate with each other because a gap is formed between 4 and 4 ′.
- the configuration of the present embodiment is such that a part (part 81) of the seal member 8 located at a position corresponding to the part with which the gear meshes (position corresponding to the position immediately above the place where the pressure change occurs) is different.
- the side plate 6 has a structure that is spread outside the step 6a.
- the force with which this part 81 pushes the side plate 6 is greater than the other parts (parts 83, 84).
- the force generated by the seal member 8 of the portion 81 to be larger than the force due to the pressure increase in the confinement region of the meshing portion of the gears 4 and 4 ′, the side plates 6 and 6 ′ , 4 'is not peeled off, so the volumetric efficiency is not lowered.
- the entire sealing member 8 has a shape that is widened to the outside of the step of the side plate 6, a large pressing force acts on the side plate 6, and there is no gap between the side plate 6 and the gears 4, 4 ′.
- the pressing force by the seal member 8 is partially increased as in the configuration of the present embodiment, the force acting on the gears 4 and 4 'can be suppressed to be small, and the increase in torque can be suppressed to the minimum. .
- the side plate 6 is expected to rise while tilting in response to an increase in pressure at the meshing portions of the gears 4 and 4 '. For this reason, the space between the gears 4, 4 ′ and the side plate 6 can be more effectively prevented by pressing the portion where the force to lift is applied.
- the gap between the side plate 6 or the seal block 7 and the case 13 is solid. Therefore, if the width of the seal member 8 is increased over the entire contour so that the pressing force is increased in the entire seal member 8, the driving torque of the gear pump 1 may vary greatly depending on the individual. However, according to the configuration of the present embodiment, only a part of the width of the seal member 8 is widened, so that the variation in the driving torque of the gear pump 1 is small.
- the side plates 6 and 6 ′ are formed of a material having a low elastic modulus such as a resin
- the width of the entire outline of the seal member 8 is widened to increase the pressing force, the side plates 6 and 6 ′ are deformed and the gears
- a force can be effectively applied to suppress the vicinity of the meshing portion.
- the seal member 8 that passes through a region closer to the rotation center of the gears 4, 4 ′ than the section where the side plates 6, 6 ′ are in contact with the seal block 7.
- a part (portion 82) of the side plate 6 and 6 ' also has a shape with an expanded cross section in the outward direction of the step.
- the reason why the region closer to the rotation center of the gears 4 and 4 'than the section where the side plates 6 and 6' and the seal block 7 are in contact is that the high-pressure liquid enters the tooth groove of the gears 4 and 4 '. Therefore, it is possible to more effectively prevent the side plates 6 and 6 'from being lifted when a pressing force is applied to a region near the rotation center, which is a portion corresponding to the space between the tooth tip and the tooth bottom.
- This configuration makes it possible to increase the force with which the seal member 8 pushes the side plate at the place where the force for peeling the side plates 6 and 6 'acts as in the case of the gears 4 and 4' meshing portion described above. As a result, the side plate is not pulled off while the pump is driven, so that the volumetric efficiency is not lowered and the increase in torque can be minimized as in the case of the closed portion of the gears 4 and 4 '.
- the configuration in which the portions 81 and 82 of the seal member 8 are widened outside the groove of the side plate 6 is because the force for peeling the side plate 6 acts on the surface. This is because 82 is similarly pressed by the surface. Thereby, the floating of the side plate 6 can be reliably prevented.
- the cross-sectional shape of the seal member 8 is the level difference between the side plates 6 and 6 ′ in both the portion 81 corresponding to the meshing portion of the gears 4 and 4 ′ and the portion 82 corresponding to the tooth tip seal portion.
- only one of the cross-sectional shapes may be configured to change (increase) the width. For example, by increasing the width only in a portion corresponding to a portion where a larger pressure fluctuation occurs, it is possible to suppress a decrease in volumetric efficiency while suppressing an increase in driving torque.
- the cross-sectional shape of the portion where the width of the seal member 8 is widened is not the same as that of the side plate 6 and the front case 11 as shown in FIG. 7, but the side plate 6, as shown in FIGS. 8 and 9 (left side). Even if a part of the width is increased between the front case 11 from the step 6 ′, substantially the same effect can be obtained.
- FIG. 9 shows a cross-sectional state of the seal member 8 before the front case 11 and the rear case 12 are assembled, and the right side shows a state after the front case 11 and the rear case 12 are assembled as the case 13.
- the seal member 8 is expanded to the outside of the step of the side plate 6 only by the height of the gap between the step of the side plate 6 and the case 13 (dimension A in FIG. 9).
- the portion 87 where the width of the seal member 8 is slightly increased at the moment when the side plate 6 is lifted off from the gears 4 and 4 ′ at a place where the force for peeling the side plate 6 acts.
- the amount of floating can be minimized.
- FIG. 10 is a perspective view of a seal member applied in the second embodiment
- FIG. 11 is an enlarged view of a G portion in FIG. 5 when the seal member shown in the second embodiment is applied before the pump assembly of the seal member (left side).
- FIG. 12 is an enlarged view of the F part of FIG. 2 when the seal member shown in the second embodiment is applied, and shows the state before the assembly (left side) and after the assembly (right side) of the seal member.
- FIG. 10 is a perspective view of a seal member applied in the second embodiment
- FIG. 11 is an enlarged view of a G portion in FIG. 5 when the seal member shown in the second embodiment is applied before the pump assembly of the seal member (left side).
- FIG. 12 is an enlarged view of the F part of FIG. 2 when the seal member shown in the second embodiment is applied, and shows the state before the assembly (left side) and after the assembly (right side) of the seal member.
- a seal member 200 is used in place of the seal members 8 and 8 'installed at the side plate steps 6a and 6a' and the seal block steps 7b and 7b '.
- the seal member 200 used in this embodiment has a shape as shown in FIG. 10 before being assembled to the gear pump 1.
- the portion 203 passes through the portion of the seal block 7, and the portion 204 passes through the teeth of the gears 4, 4 ′ of the side plates 6, 6 ′.
- the portion where the pressure change described in the first embodiment occurs that is, the portion 201 passing through the position corresponding to the portion where the gears 4 and 4 ′ mesh with each other, the side plates 6 and 6 ′, and the seal block 7 are in contact with each other.
- the portions 201 and 202 and the portions 203 and 204 are formed so that the height is gradually changed as shown in FIG. 10 so that the high portion and the low portion are smoothly connected without changing the height discontinuously. Yes. As a result, there is no gap between the step of the side plate 6 and the surface in close contact with the case 13 (the front case 11 and the rear case 12), and there is no leakage from the high pressure region to the low pressure region.
- the portions 201 and 202 are crushed at the high portions as shown in FIG.
- the side plate 6 is pushed to the gear side with a large force.
- the portions 203 and 204 are low in height before being crushed as shown on the left side of FIG. 12, they do not spread outside the step of the side plate 6 after being crushed (see the right side of FIG. 12).
- the pushing force to the side is also small.
- the side plates 6 and 6 ' are pulled from the side surfaces of the gears 4 and 4' at the locations where the pressure varies due to the rotation of the gears 4 and 4 ', as with the seal member 8 described in the first embodiment. Forces can be generated to prevent damage. Therefore, since there is no gap between the side plate 6 and the gears 4 and 4 ′, the volumetric efficiency is not lowered, and almost the same effect as described in the first embodiment can be obtained.
- the portions 201 and 202 of the seal member 200 are expanded outside the side plates 6 and 6 ′ after the pump assembly, so that the side plate 6 acting on the surface is pulled. It is possible to reliably prevent the side plate 6 from being lifted against the force to be peeled off.
- the place where a large force acts on the side plates 6, 6 ′ from the seal member 200 is a part of the seal member 200 as in the first embodiment.
- the rise can be minimized.
- Example 1 and Example 2 in a part of the seal member, the normal direction of the contour of the seal member and the cross-sectional shape of the surface perpendicular to the opposing case and side plate are It can be said that it is different from the cross-sectional shape in the other part of the seal member.
- the seal member is cut in the direction of the height of the step or the depth of the groove (depth of the notch) in a part of the seal member and in a direction perpendicular to the extending direction of the seal member. It can be said that the cross-sectional shape of the seal is different from the cross-sectional shape of the other part of the seal member.
- FIG. 13 is a perspective view of a seal member applied in the third embodiment
- FIG. 14 is an enlarged view of a portion G in FIG. 5 when the seal member shown in the third embodiment is applied before the pump assembly of the seal member (left side).
- 15 is a state diagram after assembly (right side), and FIG. 15 is an enlarged view of F part of FIG. 2 when the seal member shown in the third embodiment is applied. ) Is a state diagram.
- a seal member 300 is used instead of the seal members 8 and 8 'installed at the side plate steps 6a and 6a' and the seal block steps 7b and 7b '. Further, the heights of the side plate steps 6a and 6a 'and the seal block steps 7b and 7b' are partially changed (reduced).
- the seal member 300 of this embodiment is formed so that the cross-sectional shape in the pump shaft direction is uniform as shown in FIG.
- the heights of the side plate steps 6a and 6a ' are partially changed.
- the portion of the seal member that passes through the place where the pressure change occurs that is, the portion 301 that passes through the position corresponding to the portion where the gears 4 and 4 ′ mesh, the side plates 6 and 6 ′, and the seal block 7 come into contact with each other to seal the seal.
- the seal member 300 and the side plate 6 are smoothly connected by smoothly connecting the low step portion where the seal member portions 301 and 302 are installed and the high step portion where the seal member portions 303 and 304 are installed. , 6 ′ or the step of the seal block 7 and the gap between the case 13 (the front case 11 and the rear case 12) are prevented from leaking.
- the level difference of the side plate 6 is shallow, so that the amount of the seal member 300 to be crushed is large.
- the side plate 6 is pushed toward the gear side with a large force while spreading outside the step.
- the steps of the side plate 6 are deep in the seal member portions 303 and 304, the amount of crushing is small, and the portions 303 and 304 of the seal member 300 hardly spread outside the step of the side plate 6.
- the force of the seal member portions 303 and 304 pushing the side plate 6 toward the gear side is small.
- the side plates 6 and 6 ′ are pulled from the side surfaces of the gears 4 and 4 ′ at locations where the pressure varies due to the rotation of the gears 4 and 4 ′, as in the seal member 8 described in the first embodiment. Force can be generated to prevent it from being peeled off. Therefore, since there is no gap between the side plate 6 and the gears 4 and 4 ′, the volumetric efficiency is not lowered, and almost the same effect as described in the first embodiment can be obtained.
- the parts 301 and 302 of the seal member 300 are spread out outside the side plates 6 and 6 ′ after the pump assembly as in the first embodiment, so that the side plate 6 acting on the surface is pulled. However, it is possible to reliably prevent the side plate 6 from being lifted against the force to be applied.
- the place where a large force acts on the side plates 6, 6 ′ from the seal member 300 is a part of the seal member 300 as in the first embodiment.
- the rise can be minimized.
- Example 4 of the present invention will be described with reference to FIGS.
- the configuration and operation of the gear pump 1 in the present embodiment are the same as those in the first embodiment described in FIGS.
- a seal member 400 is used instead of the seal members 8 and 8 'installed at the side plate steps 6a and 6a' and the seal block steps 7b and 7b '.
- the side plates 6 and 6 'constituting the gear pump 1 of the present embodiment have a thin cross section or are made of a material having low rigidity such as resin. In such a side plate, even if the side plates 6 and 6 ′ are manufactured with high accuracy, the side plates 6 and 6 ′ are warped after processing because the surface contacting the gears 4 and 4 ′ is not a perfect plane due to processing limitations.
- the gear pump 1 is assembled, there is a possibility that the contact surfaces of the side plates 6, 6 'and the gears 4, 4' are not completely in contact with each other.
- the gear pump 1 is driven in this state, the high pressure region and the low pressure region communicate with each other through the gap, and the volumetric efficiency decreases.
- the side plates 406, 406 ′ are warped in a U shape, and the contact surfaces with the gears 4, 4 ′ are raised at the left and right ends of the side plates 406, 406 ′. Assume a state.
- the curvature of a side plate originates in a manufacturing method, and in the case of the same manufacturing method, the substantially same curvature will arise.
- a part of the seal member (part 401) passing through the position corresponding to the gap generated on the contact surface between the side plates 406 and 406 ′ and the gears 4 and 4 ′ due to warpage is changed to the side plate step.
- the structure has a cross-sectional shape widened outward.
- the seal member 400 is spread outside the steps of the side plates 406, 406 'at the left and right end portions of the side plates 406, 406' that are most lifted.
- a part (portion 401) of the seal member 400 at the same position as the portion where the side plates 406 and 406 ′ are lifted from the gears 4 and 4 ′ exerts a large force on the side plates 406 and 406 ′. Therefore, the side plates 406 and 406 ′ are deformed and brought into close contact with the side surfaces of the gears 4 and 4 ′. As a result, leakage during the operation of the gear pump 1 can be reduced.
- a part of the cross-sectional shape of the seal member 400 is partially expanded as shown in 401, as compared to the case where the cross section is expanded to the outside of the step or the groove of the side plate.
- the force pushing the side plates 406 and 406 ′ is reduced, so that an increase in frictional force can be minimized.
- the step height of the side plates 406, 406 ′, the height of the case 13, etc. vary from individual to individual due to manufacturing errors. Due to the variation in the height of each individual, the force with which the seal member 400 pushes the side plate also varies from individual to individual, and depending on the pump, there is a possibility that the friction is large. However, according to the seal member 400 of the present embodiment, only a part (part 401) is wide, so that there is little variation in friction when there is a manufacturing error in the pump parts.
- a part of the seal member (part 401) is configured to increase a part of the pressing force by spreading outside the step between the side plates 406 and 406 ′.
- the portion 401 of the seal member 400 is expanded in the height direction of the step between the side plates 406 and 406 ′, or the height of the step between the side plates 406 and 406 ′ on which the portion 401 of the seal member 400 is installed as described in the third embodiment. The same effect can be obtained by changing the height.
- the present embodiment and the first embodiment may be combined. That is, in addition to the portion 401 shown in FIG. 16, the width of the portion (portion 81 in FIG. 1) that passes through the portion corresponding to the portion with which the gear meshes may be increased.
- Embodiment 5 relating to an actuator to which the gear pump 1 of the present invention is applied will be described with reference to FIGS.
- the gear pump 1 of the present embodiment is used as a hydraulic pressure source for driving a cylinder 503 attached to one end of an arm 502 used in, for example, a construction machine as shown in FIG.
- the cylinder 503 includes a hydraulic pressure control unit 504 for controlling the supplied hydraulic pressure.
- the hydraulic control unit 504 is supported by the boom 501.
- the hydraulic control unit 504 includes at least a gear pump 1, an electric motor 505, a tank 506, a valve unit 507, and a control unit 508.
- the gear pump 1 is driven by the electric motor 505 based on the operator's command, the hydraulic oil is boosted, and the route for supplying the hydraulic oil to the cylinder 503 is determined by the valve unit 507, whereby the hydraulic cylinder 503 is operated and the arm 502 is moved. Make it work.
- the gear pump 1 according to the present invention is used, a pump with high volumetric efficiency can be realized without increasing the torque, so that it is not necessary to use a large electric motor. Therefore, the hydraulic pressure control unit 504 attached to the cylinder 503 becomes small and easy to install.
- Embodiment 6 relating to an actuator to which the gear pump 1 of the present invention is applied will be described with reference to FIGS.
- the gear pump 1 of the present invention can be used as a hydraulic pressure source of an actuator for steering a wheel 601 such as a robot shown in FIG.
- the steering unit 600 of the robot wheel 601 includes a cylinder 603 that adjusts the rudder angle of the wheel 601 by expanding and contracting the rod 602 with oil pressure, and a hydraulic control unit 604 that supplies oil pressure to the cylinder 603. , A control unit 605 for controlling it, an input device 606, and a sensor 607.
- the hydraulic control unit 604 includes an electric motor 608, a gear pump 1, a tank 609 for supplying oil to the pump, and a valve unit 610.
- the steering unit 600 having this configuration generates a control command value by the control unit 605 based on the operator's input and information from the sensor 607, and drives the electric motor 608 by the command value to boost the hydraulic oil by the gear pump 1. To do. Then, by operating the valve unit 610 and determining a route for supplying hydraulic oil to the cylinder 603, the cylinder 603 is expanded and contracted, and the steering angle of the wheel 601 attached to the tip of the rod 602 is operated.
- the gear pump 1 of the present invention If the gear pump 1 of the present invention is used, it is not necessary to use a large electric motor as in the fifth embodiment. Therefore, the hydraulic control unit 604 attached to the cylinder 603 becomes small and easy to install.
- the configuration using the gear pump 1 of the present invention can be used as a hydraulic pressure source for actuators of various machines such as robots, construction machines, and automobiles.
- the present invention includes various solutions, but a configuration example in which the present invention is applied to a gear pump can be summarized as follows.
- a pump assembly a case for housing the pump assembly, and a cutout (step or groove) formed on the side plate and the seal block on the opposite side of the gear, and between the case And a seal member that separates the high-pressure part and the low-pressure part inside the case, and when the pump assembly is assembled in the case, a part of the seal member is normal to the contour of the seal member
- the cross-sectional shape of the direction and the face perpendicular to the case and the side plate is different from the cross-sectional shape of the other part of the seal member.
- a portion of the seal member having a different cross-sectional shape is a section where the seal block is in contact with the side plate (even in a section where the seal block covers a part of the gear in the circumferential direction). A portion that passes through a region near the gear rotation center.
- the portion of the seal member having a different cross-sectional shape is a position corresponding to a gap generated between the gear side surface and the side plate due to warpage of the side surface.
- the portion having a different cross-sectional shape of the seal member has a cross-sectional shape that spreads outside the groove or step of the side plate or the seal block, rather than other portions. .
- the portion having a different cross-sectional shape of the seal member is a cross-section in which the depth of the groove of the side plate or the height in the height direction of the step is larger than the other portions. Has a shape.
- a part of the seal member is formed using a material having a different elastic modulus instead of a portion having a different cross-sectional shape of the seal member.
- a part of the seal member is formed by using a material having a different elastic modulus in a portion where the cross-sectional shape of the seal member is different.
- a seal member formed substantially uniformly is used, and the cross-sectional shape of the seal member is different. A groove or a step of the side plate is formed shallower than other portions.
- the seal is compared with a case where the force is increased by changing the width of the cross-sectional shape in the entire contour of the seal member.
- the difference in pressing force on the side plate generated by the member is small, and the individual difference in driving torque for each gear pump is small.
- a particularly efficient gear pump can be realized with respect to the configured gear pump. Since the gear pump to which the present invention is applied can be driven with high response and high pressure by a small motor, the entire system including the actuator equipped with the gear pump can be miniaturized.
- this invention is not limited to the above-mentioned Example, Various modifications are included.
- the above-described embodiments have been described in detail for easy understanding of the present invention, and are not necessarily limited to those having all the configurations described.
- a part of the configuration of one embodiment can be replaced with the configuration of another embodiment, and the configuration of another embodiment can be added to the configuration of one embodiment.
- a portion corresponding to a portion where the pressure fluctuation is large is formed of a material having a high elastic modulus, thereby partially increasing the pressing force. You may make it do. Moreover, you may make it have the shape of the sealing member as described in Example 1 and Example 2 together. Further, the shape of the sealing member described in the first, second, and fourth embodiments may be combined with the shape of a step such as a side plate described in the third embodiment.
- the present invention is similarly applied to a gear motor that moves a gear in reverse from a liquid flow.
- the external gear pump in which two external gears are combined has been described.
- the present invention can be similarly applied to an internal gear pump in which internal gears and external gears are combined. Even in these cases, the portion where the pressure fluctuation occurs, that is, the width of the seal member at the portion corresponding to the meshing portion of the gear, etc. is increased so that the force pushing the side plate toward the gear side is partially increased. Thus, the same effect as that of the above-described embodiment can be obtained.
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Abstract
Description
また、本実施例ではシール部材8を同一の材料で形成する場合を説明したが、一部の材料を変更することにより、押付力を部分的に変更(大きく)するようにしてもよい。例えば、本実施例で説明した側板6,6’の段差の外側に広げる部分81,82を弾性率の高い材料で形成することにより、この部分で大きな力を発生させ、側板6,6’をギヤ4,4’に大きな力で押し付ける構成としてもほぼ同じ効果を得ることができる。
(1) 互いに噛み合い、駆動源によって回転駆動されるギヤ、前記ギヤの側面に隣接して配置される側板、前記側板と接触し、前記ギヤの円周方向の一部と接触するシールブロックを備えるポンプ組立体と、前記ポンプ組立体を収容するケースと、前記側板と前記シールブロックの前記ギヤとは反対側に形成された切り欠き部(段差または溝)に沿って設置され、ケースとの間で密着し、ケース内部の高圧部分と低圧部分を区画するシール部材とを備え、前記ポンプ組立体が前記ケース内に組み込まれた時に、前記シール部材の一部は、シール部材の輪郭の法線方向、かつ、対向する前記ケースと前記側板に垂直な面の断面形状が、前記シール部材の他の部分の断面形状と異なる。
(2) (1)において、前記シール部材の前記断面形状が異なる部分は、前記ギヤの噛合う部分に対応する位置である。
(3) (1)において、前記シール部材の前記断面形状が異なる部分は、前記シールブロックが前記側板と接触している区間(前記シールブロックが前記ギヤの円周方向の一部を覆う区間でもある)の前記ギヤ回転中心寄りの領域を通過する部分である。
(4) (1)において、前記シール部材の前記断面形状が異なる部分は、前記側面の反りなどに起因して、前記ギヤ側面と前記側板間で生じた隙間に対応する位置である。
(5) (1)~(4)の何れかにおいて、前記シール部材の断面形状が異なる部分は、他の部分よりも前記側板或いは前記シールブロックの溝又は段差の外側に広がった断面形状を有する。
(6) (1)~(4)の何れかにおいて、前記シール部材の断面形状が異なる部分は、他の部分よりも前記側板の溝の深さ又は段差の高さ方向の高さが大きい断面形状を有する。
(7) (1)~(4)の何れかにおいて、前記シール部材の一部は、前記シール部材の前記断面形状が異なる部分に代えて、弾性率の異なる材料を用いて形成される。または、前記シール部材の一部は、前記シール部材の断面形状が異なる部分が、さらに弾性率の異なる材料を用いて形成される。
(8) (1)~(4)の何れかにおいて、前記シール部材に代えて、実質的に全体を一様に形成したシール部材を用い、前記シール部材の前記断面形状が異なる部分に対応する前記側板の溝又は段差が他の部分に比べて浅く形成される。
(1) ポンプ駆動中に側板をギヤ側面から引きはがそうとする力が作用する場所に対して、シール部材の一部が大きな荷重を発生するため、側板がギヤ側面から引きはがされることがなく、ポンプの容積効率が低下することがない。また、局所的なポンプの圧力変動の影響に対して必要な箇所に限定してシール部材が発生する力を大きくするため、側板の浮き上がりを防止するために側板に作用させる力が必要最低限でよい。また、シールブロックまたは側板の切り欠き部(段差または溝)の高さが製造誤差によって異なる場合、シール部材の全輪郭で断面形状の幅を変更して力を大きくする場合と比較して、シール部材が発生する側板を押しつける力の差が小さく、ギヤポンプ毎の駆動トルク個体差が少ない
(2) 小さな隙間が大きな容積効率低下の原因となる小型ポンプや、側板が樹脂などの剛性の低い部材で構成されるギヤポンプに対して、特に効果を発揮し、高効率なギヤポンプを実現できる。本発明を適用したギヤポンプは、小型モータで高応答かつ高圧力で駆動することができるため、ギヤポンプを搭載したアクチュエータを含むシステム全体を小型化することが可能となる。
2 ドライブシャフト
3 ドリブンシャフト
4,4’ ギヤ
5 駆動ピン
6,6’ 側板
7 シールブロック
8,8’ シール部材
9 ノックピン
10 ポンプ組立体
11 フロントケース
12 リアケース
13 ケース
14 付勢機構
16 ケースシール
18 オイルシール
19 吸入ポート
20 吐出ポート
200,300,400 シール部材
Claims (9)
- 一対のギヤ、前記ギヤの側面に配置された側板、前記ギヤの円周方向の一部を覆うように配置されたシールブロックから構成された組立体と、
前記組立体を収容するケースと、
前記側板または前記シールブロックと前記ケースとの間に設置され、かつ前記側板または前記シールブロックに形成された切り欠き部に沿って設置され、前記ケース内部の高圧部分と低圧部分を区画するシール部材とを備え、
前記組立体が前記ケース内に組み込まれた時に、前記シール部材による前記側板を前記ギヤ方向に押す力が前記シール部材の設置位置に応じて部分的に大きくなるように、前記シール部材または前記切り欠き部が構成されていることを特徴とする回転型流体機械。 - 請求項1に記載の回転型流体機械において、
前記シール部材による前記側板を前記ギヤ方向に押す力を部分的に大きくする位置は、前記ギヤの噛合う部分に対応する位置であることを特徴とする回転型流体機械。 - 請求項1に記載の回転型流体機械において、
前記シール部材による前記側板を前記ギヤ方向に押す力を部分的に大きくする位置は、前記シールブロックが前記ギヤの円周方向の一部を覆う区間の前記ギヤ回転中心寄りの領域に対応する位置であることを特徴とする回転型流体機械。 - 請求項1に記載の回転型流体機械において、
前記シール部材による前記側板を前記ギヤ方向に押す力を部分的に大きくする位置は、前記組立体が前記ケース内に組み込まれる前の状態において、前記ギヤの側面と前記側板間に生じた隙間に対応する位置であるであることを特徴とする回転型流体機械。 - 請求項2~4の何れかに記載の回転型流体機械において、
前記シール部材による前記側板を前記ギヤ方向に押す力を部分的に大きくする位置に対応する位置に設置される前記シール部材の部分は、前記切り欠き部の深さ方向で、かつ、前記シール部材の延伸方向と垂直な方向に切断した前記シール部材の断面形状が、前記シール部材の他の部分の前記断面形状と異なるように形成されていることを特徴とする回転型流体機械。 - 請求項5に記載の回転型流体機械において、
前記断面形状が異なる前記シール部材の部分は、前記他の部分よりも、前記切り欠き部の外側に広がった断面形状を有することを特徴とする回転型流体機械。 - 請求項5に記載の回転型流体機械において、
前記断面形状が異なる前記シール部材の部分は、前記他の部分よりも、前記切り欠き部の深さ方向の高さが大きい断面形状を有することを特徴とする回転型流体機械。 - 請求項2~4の何れかに記載の回転型流体機械において、
前記シール部材による前記側板を前記ギヤ方向に押す力を部分的に大きくする位置に対応する位置に設置される前記シール部材の部分は、前記シール部材の他の部分の弾性率よりも高い弾性率を有する材料を用いて形成されていることを特徴とする回転型流体機械。 - 請求項2~4の何れかに記載の回転型流体機械において、
前記シール部材による前記側板を前記ギヤ方向に押す力を部分的に大きくする位置に対応する位置に形成される前記切り欠き部の部分は、前記切り欠き部の他の部分に比べて浅く形成されていることを特徴とする回転型流体機械。
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PCT/JP2013/051844 WO2014118876A1 (ja) | 2013-01-29 | 2013-01-29 | 回転型流体機械 |
US14/764,104 US9828993B2 (en) | 2013-01-29 | 2013-01-29 | Rotary fluid machine |
JP2014559375A JP6006811B2 (ja) | 2013-01-29 | 2013-01-29 | 回転型流体機械 |
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PCT/JP2013/051844 WO2014118876A1 (ja) | 2013-01-29 | 2013-01-29 | 回転型流体機械 |
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PCT/JP2013/051844 WO2014118876A1 (ja) | 2013-01-29 | 2013-01-29 | 回転型流体機械 |
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US (1) | US9828993B2 (ja) |
JP (1) | JP6006811B2 (ja) |
WO (1) | WO2014118876A1 (ja) |
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JPH0842461A (ja) * | 1994-07-27 | 1996-02-13 | Kayaba Ind Co Ltd | ギヤポンプ |
JPH09287576A (ja) * | 1996-04-17 | 1997-11-04 | Kubota Corp | ギアポンプ並びにそのシール部材 |
JPH11303768A (ja) * | 1998-04-22 | 1999-11-02 | Koyo Seiko Co Ltd | ギヤポンプ |
JP2000064967A (ja) * | 1998-08-20 | 2000-03-03 | Koyo Seiko Co Ltd | ギヤポンプ |
JP2009216070A (ja) * | 2008-03-13 | 2009-09-24 | Hitachi Ltd | ギヤポンプのシール装置 |
JP2012017743A (ja) * | 2011-10-07 | 2012-01-26 | Hitachi Automotive Systems Ltd | ギヤポンプ |
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US2707441A (en) * | 1952-07-01 | 1955-05-03 | Commercial Shearing | Rotary pump or motor |
US3050010A (en) * | 1960-02-23 | 1962-08-21 | Thompson Ramo Wooldridge Inc | Pressure loaded pump |
US3416459A (en) * | 1966-05-24 | 1968-12-17 | Parker Hannifin Corp | Rotary pump or motor |
DE2403319A1 (de) * | 1974-01-24 | 1975-07-31 | Bosch Gmbh Robert | Zahnradmaschine |
US5022837A (en) * | 1989-11-13 | 1991-06-11 | Sta-Rite Industries, Inc. | Seal arrangement for a gear machine |
JP3932595B2 (ja) | 1997-03-12 | 2007-06-20 | 株式会社日立製作所 | ギヤポンプ |
JP4931952B2 (ja) | 2009-03-24 | 2012-05-16 | 日立オートモティブシステムズ株式会社 | ギヤポンプ |
-
2013
- 2013-01-29 WO PCT/JP2013/051844 patent/WO2014118876A1/ja active Application Filing
- 2013-01-29 JP JP2014559375A patent/JP6006811B2/ja not_active Expired - Fee Related
- 2013-01-29 US US14/764,104 patent/US9828993B2/en active Active
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
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JPH0842461A (ja) * | 1994-07-27 | 1996-02-13 | Kayaba Ind Co Ltd | ギヤポンプ |
JPH09287576A (ja) * | 1996-04-17 | 1997-11-04 | Kubota Corp | ギアポンプ並びにそのシール部材 |
JPH11303768A (ja) * | 1998-04-22 | 1999-11-02 | Koyo Seiko Co Ltd | ギヤポンプ |
JP2000064967A (ja) * | 1998-08-20 | 2000-03-03 | Koyo Seiko Co Ltd | ギヤポンプ |
JP2009216070A (ja) * | 2008-03-13 | 2009-09-24 | Hitachi Ltd | ギヤポンプのシール装置 |
JP2012017743A (ja) * | 2011-10-07 | 2012-01-26 | Hitachi Automotive Systems Ltd | ギヤポンプ |
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US9828993B2 (en) | 2017-11-28 |
JP6006811B2 (ja) | 2016-10-12 |
JPWO2014118876A1 (ja) | 2017-01-26 |
US20150322945A1 (en) | 2015-11-12 |
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