WO2017159135A1 - Hydraulic device - Google Patents

Hydraulic device Download PDF

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Publication number
WO2017159135A1
WO2017159135A1 PCT/JP2017/004688 JP2017004688W WO2017159135A1 WO 2017159135 A1 WO2017159135 A1 WO 2017159135A1 JP 2017004688 W JP2017004688 W JP 2017004688W WO 2017159135 A1 WO2017159135 A1 WO 2017159135A1
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WO
WIPO (PCT)
Prior art keywords
region
pair
hydraulic
sliding contact
gears
Prior art date
Application number
PCT/JP2017/004688
Other languages
French (fr)
Japanese (ja)
Inventor
竹田　博昭
Original Assignee
住友精密工業株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 住友精密工業株式会社 filed Critical 住友精密工業株式会社
Priority to CN201780003969.6A priority Critical patent/CN108291539B/en
Publication of WO2017159135A1 publication Critical patent/WO2017159135A1/en

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Classifications

    • 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
    • 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

Definitions

  • the present invention relates to a hydraulic pump provided with a pair of helical gears whose tooth portions mesh with each other.
  • the hydraulic pump 1 includes a housing 2 in which a hydraulic chamber 4 is formed, and a pair of helical gears disposed in the hydraulic chamber 4.
  • Helical gears each having a tooth shape in which an arc portion is included in the tooth tip and the tooth bottom and a continuous contact line is formed from one end portion to the other end portion in the tooth width direction at the meshing portion, that is, Continuous contact line meshing gears (hereinafter simply referred to as “gears”) 20 and 25, bushes 40 and 45 as a pair of bearing members, and a pair of side plates 30 and 35 are provided.
  • the housing 2 includes a main body 3 in which the hydraulic chamber 4 having a space whose cross-sectional shape is similar to an Arabic numeral “8” is formed from one end face to the other end face.
  • a front cover 7 fixed to one end face (front end face) via a seal 11 in a liquid-tight manner, and an end cover fixed to the other end face (rear end face) of the main body 3 via a seal 12 in the same manner.
  • the hydraulic chamber 4 is closed by the front cover 7 and the end cover 8 as a pair of cover bodies.
  • One of the pair of gears 20 and 25 is a drive gear 20 and the other is a driven gear 25.
  • the gear 20 has rotary shafts 21 and 22 extending from its both end surfaces along its central axis.
  • the gear 25 has its rotary shafts 26 and 27 extending from its both end surfaces along its central axis.
  • the pair of gears 20 and 25 are inserted into the hydraulic pressure chamber 4 in mesh with each other, and their tooth tips come into sliding contact with the inner peripheral surface 3 a of the hydraulic pressure chamber 4.
  • the hydraulic chamber 4 is divided into a high pressure side and a low pressure side with the meshing portion of the pair of gears 20 and 25 as a boundary.
  • end 21a of the rotary shaft 21 on the front side of the drive gear 20 is formed in a taper shape, and further, a screw portion 21b is formed at the tip thereof, and this portion is a through-hole formed in the front cover 7. It extends outward through the hole 7a, and the oil seal 10 seals between the outer peripheral surface of the rotary shaft 21 and the inner peripheral surface of the through hole 7a.
  • a perspective view of the gears 20 and 25 is shown in FIG.
  • the main body 3 is formed with an intake hole (intake channel) 5 that communicates with the low pressure side of the hydraulic pressure chamber 4 on one side surface, and the hydraulic pressure chamber 4 is also formed on the other side surface opposite to this.
  • a discharge hole (discharge flow path) 6 leading to the high pressure side is formed.
  • the intake hole 5 and the discharge hole 6 are provided so that their respective axes are located at the center between the pair of gears 20 and 25.
  • the side plates 30 and 35 are made of plate-like members formed in a shape imitating the Arabic numeral “8”, and the side plates 30 are formed with through holes 31 and 32. Through holes 36 and 37 are formed in 35.
  • the side plate 30 is disposed on the front side of the gears 20 and 25 in a state where the rotary shaft 21 is inserted into the through hole 31 and the rotary shaft 26 is inserted into the through hole 32. Is in contact with the entire front end surface including the teeth of the gears 20 and 25.
  • the side plate 35 is disposed on the rear side of the gears 20 and 25 with the rotary shaft 22 inserted through the through-hole 36 and the rotary shaft 27 inserted through the through-hole 37. The surface is in contact with the entire rear end surface including the teeth of the gears 20 and 25.
  • the side plate 30 is formed with lubrication grooves 33 and 34 communicating with the inner and outer surfaces of the through holes 31 and 32, and similarly, the side plate 35 has an inner surface of the through holes 36 and 37.
  • Lubricating grooves 38 and 39 communicating with the front and back sides are formed.
  • the bushes 40 and 45 are bearings formed in a shape imitating the Arabic numeral “8”, and support holes 41 and 42 are formed in the bush 40.
  • support holes 46 and 47 are formed in the bush 45.
  • the bush 40 is disposed on the front side of the side plate 30 with the rotating shaft 21 inserted through the support hole 41 and the rotating shaft 26 inserted through the support hole 42.
  • seal grooves 40a and 45a having a shape imitating the Arabic numeral “3” are formed on the end surfaces of the bushes 40 and 45 facing the side plates 30 and 35, respectively.
  • partition seals 50 and 55 having elasticity are disposed in the seal grooves 40a and 45a, respectively.
  • the partition seal 50 partitions a rear region 51, which is a gap between the bush 40 and the side plate 30, into a high pressure side region 51 a and a low pressure side region 51 b, and the partition seal 55 is formed between the bush 45 and the side plate 35.
  • a back surface region 56 which is a gap therebetween, is partitioned into a high pressure side region 56a and a low pressure side region 56b.
  • the hydraulic oil on the high pressure side of the hydraulic pressure chamber 4 is guided to the high pressure side regions 51a and 56a of the back surface regions 51 and 56 partitioned by the partition seals 50 and 55 through an appropriate flow path.
  • the side plates 30 and 35 are pressed against the end surfaces of the gears 20 and 25 by the high-pressure hydraulic oil guided to the high-pressure side regions 51a and 56a, respectively. Oil is prevented from leaking to the low pressure side.
  • the high pressure hydraulic oil in the hydraulic chamber 4 also acts on the side plates 30 and 35 on the end surfaces of the gears 20 and 25, but the pressure receiving areas in the high pressure spaces 51a and 56a are as follows. As a result, the side plates 30 and 35 are pressed against the end surfaces of the gears 20 and 25 due to the difference in their acting forces.
  • both end portions of the partition seals 50 and 55 are folded outward and folded back portions 50a and 55a.
  • the folded portions 50a and 55a are The side plates 30 and 35, the inner peripheral surface 3a of the main body 3 constituting the hydraulic chamber 4, and the bushes 40 and 45 (more precisely, the bottom surfaces of the seal grooves 40a and 45a) are in liquid-tight contact.
  • the front end surface of the bush 40 is in contact with the end surface of the front cover 7, and the rear end surface of the bush 45 is in contact with the end surface of the end cover 8, whereby the end surfaces of the gears 20, 25 and the side plates 30, 35 are connected.
  • the abutting state and the side plates 30, 35 and the partition seals 50, 55 provided on the bushes 40, 45 are in contact with each other, and the gears 20, 25, the side plates 30, 35, the partition seals 50, 55.
  • a preload is applied to the bushes 40 and 45.
  • the partition seals 50 and 55 are elastically deformed by the applied pressure, and are in liquid-tight contact with the side plates 30 and 35 and the bushes 40 and 45 by the elastic force.
  • the pipe connected to the hydraulic oil storage tank is connected to the intake hole 5 of the housing 2, and the pipe connected to the hydraulic equipment is connected to the discharge hole 6.
  • a drive motor is connected to the rotary shaft 21 of the drive gear 20, and then the drive gear 20 is rotated by the drive motor.
  • the driven gear 25 meshed with the drive gear 20 rotates, and the hydraulic oil in the region sandwiched between the inner peripheral surface 3a of the hydraulic chamber 4, the teeth of the gears 20, 25 and the side plates 30, 35 is transferred to the gear.
  • 20 and 25 are transferred to the discharge hole 6 side, and the discharge hole 6 side becomes the high-pressure side and the intake hole 5 side becomes the low-pressure side with the meshing portion of the gears 20 and 25 as the boundary.
  • the hydraulic oil on the low pressure side surrounded by the inner peripheral surface 3a of the hydraulic chamber 4, the teeth of the gears 20 and 25, and the side plates 30 and 35 is moved to the high pressure side with high efficiency.
  • the hydraulic pump 1 is assembled, it is transferred in order to transfer, i.e., transfer between the teeth of the gears 20 and 25 and the inner peripheral surface 3a of the hydraulic chamber 4 as much as possible.
  • a preliminary operation is generally performed in which the inner peripheral surface 3a of the hydraulic chamber 4 is cut (self-cut) by the teeth of the gears 20 and 25.
  • the hydraulic pump 1 When assembled, the hydraulic pump 1 is finished such that the inner diameters of the support holes 41, 42, 46, 47 of the bushes 40, 45 are larger than the outer diameters of the rotary shafts 21, 22, 26, 27 by a predetermined amount.
  • the gears 20 and 25 are in contact with the inner peripheral surface 3 a on the low pressure side of the hydraulic chamber 4. Therefore, when such a hydraulic pump 1 is placed under the above-described use mode as a preliminary operation, the gears 20 and 25 are pushed to the low pressure side by the high pressure hydraulic oil, and the tooth tips thereof are on the low pressure side of the hydraulic chamber 4.
  • the inner peripheral surface 3 a is pressed by the inner peripheral surface 3 a, and the inner peripheral surface 3 a on the low pressure side is cut by the tooth tips of the gears 20 and 25. Then, when the inner peripheral surface 3a is cut by the gears 20, 25 by an amount movable to the low pressure side, the cutting is finished, and the tooth tips of the gears 20, 25 are in sliding contact with the inner peripheral surface 3a. Realized.
  • FIG. 13 shows a state in which the inner peripheral surface 3a of the hydraulic chamber 4 is self-cut by such preliminary operation.
  • FIG. 13 shows an outline and corresponds to a cross-sectional view in the direction of arrow BB in FIG.
  • the gears 20 and 25 are pressed in a substantially horizontal direction (arrow E and F directions) to cut the inner peripheral surface 3a of the hydraulic chamber 4, and the gear 20 is a vertical reference.
  • the tooth tip of the gear 20 is not in sliding contact with the inner peripheral surface 3a.
  • gear 25 is in sliding contact with the inner peripheral surface 3a in an angular range (sliding angle range) theta b3 from the angle theta b1 toward the rotational direction (arrow D b direction) from the reference line r through an angle theta b2 In the range exceeding the angle ⁇ b2 , the tooth tip of the gear 25 is not in sliding contact with the inner peripheral surface 3a.
  • the sliding contact angle range ⁇ a3 , ⁇ b3 within the region surrounded by the inner peripheral surface 3 a of the hydraulic chamber 4, the tooth surfaces of the gears 20, 25 and the side plates 30, 35 (referred to as “hydraulic region”).
  • the hydraulic fluid in the hydraulic pressure region in the inside has a low pressure P L , and the hydraulic fluid in the hydraulic pressure region in the range exceeding the sliding contact angle range ⁇ a3 , ⁇ b3 in the rotation direction (arrow D a , D b direction) is high pressure. the P H.
  • the tooth tips of the gears 20 and 25 can be brought into sliding contact with the inner peripheral surface 3a on the low pressure side of the hydraulic pressure chamber 4, and thus the tooth tips of the gears 20 and 25 are brought into contact with each other.
  • the low-pressure side hydraulic oil surrounded by the inner peripheral surface 3a of the hydraulic chamber 4 the teeth of the gears 20 and 25, and the side plates 30 and 35 is highly efficient. It can be transferred to the high pressure side.
  • the gear 20 is provided at the end of the sliding contact.
  • a high-pressure side is provided via a gap formed between the inner peripheral surface 3a, the side plates 30, 35 and the tooth portions of the gears 20, 25.
  • the gears 20 and 25 are helical gears, the gap is gradually increased due to the twist of the tooth portion.
  • the working liquid flowing in from a very small gap becomes a jet directed toward the side plate 35, and this jet causes erosion (erosion) on the surface of the side plate 35.
  • FIGS. 14 (a) to (c) are views in the direction of arrow C in FIG. 12 and illustrate the gear 20, but the same applies to the gear 25. It is attached in writing.
  • Reference numerals 20 a1 (25 a1 ), 20 a2 (25 a2 ), 20 a3 (25 a3 ), and 20 a4 (25 a4 ) are respectively the top portions (ridge lines ) of the tooth portions.
  • the gear 20 (25) is a helical gear
  • the tooth trace is twisted, so that the tooth tip of the gear 20 (25) is separated from the inner peripheral surface 3a of the hydraulic chamber 4 at the end of the sliding contact.
  • the part that first creates a gap is the side plate on the side in which the direction toward the side plates 30 and 35 along the teeth of the gear 20 (25) is the forward direction with respect to the rotation direction of the gear 20 (25). (In this example, the side plate 35).
  • the gear 20 (25) rotates in the direction indicated by the arrow D a (D b ), and in FIG. 14 (a), the top portion located upstream from the sliding contact end CE a (CE b ) indicated by a two-dot chain line.
  • 20 a2 (25 a2 ), 20 a3 (25 a3 ), and 20 a4 (25 a4 ) are in sliding contact with the inner peripheral surface 3 a of the hydraulic chamber 4, while the sliding contact end CE a (CE b ) Exceeding the top portion 20 a1 (25 a1 ), at least a part thereof is not in sliding contact with the inner peripheral surface 3 a.
  • the hydraulic oil between the top 20 a1 (25 a1 ) and the top 20 a2 (25 a2 ) is high pressure P H , the top 20 a2 (25 a2 ) and the top.
  • the hydraulic fluid between 20 a3 (25 a3 ) has a low pressure P L
  • the hydraulic fluid between the top 20 a3 (25 a3 ) and the top 20 a4 (25 a4 ) has a low pressure P L.
  • the gear 20 (25) rotates in the direction of the arrow D a (D b ), and the rotation direction (arrow D a () of the top 20 a2 (25 a2 ).
  • D b ) direction When the tip part exceeds the sliding contact end CE a (CE b ) and a gap is formed between the top part 20 a2 (25 a2 ), the inner peripheral surface 3 a and the side plate 35, a broken arrow
  • the hydraulic oil flows into the tooth gap between the top portion 20 a2 (25 a2 ) and the top portion 20 a3 (25 a3 ) as a jet flow toward the side plate 35 from this gap.
  • the present invention has been made in view of the above circumstances, and is a hydraulic pump using a helical gear, which can effectively suppress the occurrence of erosion on the side plate.
  • the purpose is to provide.
  • the pair of helical gears are configured to be in sliding contact with the inner peripheral surface of the hydraulic chamber, respectively, in a predetermined sliding contact angle range on the rotational direction side from the meshing portion, and the pair of side plates,
  • the hydraulic pressure region surrounded by the tooth surfaces of the pair of helical gears and the inner peripheral surface of the hydraulic pressure chamber is directed from the meshing portion toward the rotational direction with the meshing portion as a boundary, and the entire top portion is in the hydraulic pressure chamber.
  • the region up to the foremost tooth part that is in sliding contact with the inner peripheral surface of is set to be low pressure, and the region in the rotational direction forward from the tooth part is set to be high pressure,
  • Each of the back regions divided into two regions by the seal member is set to a higher pressure than the other region, with one of the regions communicating with the high pressure hydraulic region.
  • this hydraulic pump is configured such that the pair of helical gears are in sliding contact with the inner peripheral surface of the hydraulic chamber, respectively, within a predetermined sliding contact angle range on the rotational direction side from the meshing portion. ing.
  • the hydraulic region surrounded by the pair of side plates, the tooth surfaces of the pair of helical gears and the inner peripheral surface of the hydraulic chamber is directed from the meshing portion toward the rotation direction with the meshing portion as a boundary, and the entire top portion is liquid.
  • a region to the foremost tooth portion that is in sliding contact with the inner peripheral surface of the pressure chamber has a low pressure, and a region in front of the rotation direction from the tooth portion has a high pressure.
  • Each of the back regions divided into two regions by the seal member is set to a high pressure of the same pressure as the high pressure side of the hydraulic pressure region, with at least one of the rear regions communicating with the high pressure hydraulic pressure region.
  • the range of the high pressure region which is one of the regions, extends to the region corresponding to the sliding contact angle range.
  • the side plate along the helical line of the helical gear is directed to each side plate in the forward direction with respect to the rotating direction of the helical gear.
  • through holes penetrating the front and back are respectively drilled at positions corresponding to the high pressure region of the back surface region, and the sliding contact angle within the range, the foremost tooth portion in the rotation direction of the helical gear, the following tooth portion, the pair of side plates and the low pressure region surrounded by the inner peripheral surface of the hydraulic chamber, and the high pressure region of the back region
  • it is comprised so that it may communicate through this through-hole.
  • the tooth portion of the helical gear that rotates in a predetermined direction, and the tooth portion within the sliding contact angle range, that is, the entire top portion of the tooth portion is the hydraulic chamber.
  • the foremost tooth portion in the rotational direction moves beyond the sliding contact angle range and moves to the outside of the tooth portion.
  • the high-pressure working liquid in the back region flows into the low-pressure region (rear region) surrounded by the pair of side plates and the inner peripheral surface of the hydraulic chamber through the through hole. It becomes.
  • the high-pressure working liquid in the back region flows into the rear region through the through-hole, but the inflow direction is a direction substantially along the tooth surface of the tooth portion. Is unlikely to cause erosion.
  • the diameter of each through hole is expanded toward the helical gear side.
  • the hydraulic pump according to the present invention before the foremost tooth portion within the sliding contact angle range out of the helical gear tooth portion exceeds the sliding contact angle range and goes outside. Since the high-pressure hydraulic fluid in the back region flows into the rear region of the tooth part through the through-hole provided in the side plate, the rear region becomes high pressure, and the regions before and after the tooth part have the same high pressure.
  • the front tooth part exceeds the sliding contact angle range and leaves the inner peripheral surface of the hydraulic chamber, even if a gap is formed between the inner peripheral surface, the side plate and the helical gear tooth part, The phenomenon that hydraulic oil flows in from the formed gap toward the rear region does not occur, and thus the conventional problem of erosion of the side plate does not occur.
  • FIG. 1 is a front sectional view showing a hydraulic pump according to an embodiment of the present invention.
  • FIG. 2 is a cross-sectional view in the direction of arrow A′-A ′ in FIG. 1. It is the side view which showed the side plate which concerns on this embodiment. It is explanatory drawing which showed the shape of the through-hole formed in a side plate. It is explanatory drawing for demonstrating the effect
  • FIG. 7 is a cross-sectional view in the direction of arrow AA in FIG. 6. It is the side view which showed the side plate of the conventional hydraulic pump shown in FIG. It is the front view which showed the bush of the conventional hydraulic pump shown in FIG. FIG.
  • FIG. 10 is a right side view of the bush shown in FIG. 9. It is the right view which showed the state which mounted
  • FIG. 7 is a perspective view showing a helical gear, a side plate, and a bush of the conventional hydraulic pump shown in FIG. 6. It is sectional drawing of the arrow BB direction in FIG. It is explanatory drawing for demonstrating the problem in the conventional hydraulic pump.
  • FIG. 1 is a front sectional view showing a hydraulic pump according to an embodiment of the present invention
  • FIG. 2 is a sectional view in the direction of arrow A′-A ′ in FIG. 1.
  • 3 is a side view showing a side plate according to the hydraulic pump of this example
  • FIG. 4 is an explanatory view showing the shape of a through hole formed in the side plate
  • FIG. 5 is a hydraulic diagram of this example. It is explanatory drawing for demonstrating the effect
  • the hydraulic pump 100 of this example has the same configuration as the conventional hydraulic pump 1 shown in FIGS. 6 to 13 except for the configuration of the side plate 135. Accordingly, in FIGS. 1 to 5, the same components as those of the conventional hydraulic pump 1 are denoted by the same reference numerals, and the above description is applied to the same components, and the detailed description thereof will be omitted below. . Also in the hydraulic pump 100 of this example, as in the conventional hydraulic pump 1, self-cutting is performed by preliminary operation, and the gears 20 and 25 are in sliding contact with the inner peripheral surface 3 a of the hydraulic chamber 4. ing.
  • the configuration of the side plate 135 is different from the configuration of the side plate 35 of the conventional hydraulic pump 1.
  • the side plate 135 is such that the direction toward the side plate 135 along the teeth of the gears 20 and 25 is the forward direction with respect to the rotation direction of the gears 20 and 25.
  • the direction of the side plate 30 toward the side plate 30 along the teeth of the gears 20 and 25 is opposite to the rotation direction of the gears 20 and 25.
  • the side plate 135 has the same external shape as the side plate 35 illustrated in FIG. 8, and is different from the side plate 35 in that through holes 135 a and 135 b that penetrate the front and back surfaces. It is only a point provided with.
  • Reference numerals 136 and 137 are through holes corresponding to the through holes 36 and 37, and reference numerals 138 and 139 are lubrication grooves corresponding to the lubricating grooves 38 and 39, respectively.
  • the through hole 135a as well as located in the sliding angle range theta a3 gear 20 described above, is provided at a position leading to the high pressure region 56a of the rear region 56 partitioned by the partition seal 55.
  • through hole 135b, as well as position the sliding contact angle range ⁇ in b3 gear 25 is provided at a position leading to the high pressure region 56a of the rear region 56 partitioned by the partition seal 55.
  • the partition seal 55 is a seal that partitions the back region 56 formed between the bush 45 and the side plate 135 into a high-pressure region 56a and a low-pressure region 56b. As shown in FIG. region 56a of are extend to the inside of the sliding angle range theta a3 gear 20, and a region corresponding to the inside of the sliding angle range theta b3 gear 25.
  • the position where the angle ⁇ a1 is from the vertical reference line r is the position where the gear 20 starts sliding contact with the inner peripheral surface 3 a of the hydraulic chamber 4 and the angle ⁇ from the reference line r.
  • the position that becomes a2 is a position at which the sliding contact ends.
  • the position at the angle ⁇ b1 from the reference line r is the position at which the gear 25 starts sliding contact with the inner peripheral surface 3a of the hydraulic chamber 4, and the position at the angle ⁇ b2 from the reference line r is This is the position where the sliding contact ends.
  • CE a indicates a position where the gear 20 ends sliding contact
  • CE b indicates a position where the gear 25 ends sliding contact.
  • These through-holes 135a and 135b are generally round holes as shown in FIG. 4 (a). However, as a modification, the through-holes 135a and 135b are arranged on the gears 20 and 25 side as shown in FIG. 4 (b).
  • the shape may be chamfered (through holes 135a ′ and 135b ′), or may be a tapered shape (through holes 135a ′′ and 135b ′′) whose diameter is increased toward the gears 20 and 25 as shown in FIG. good.
  • the pipe connected to the hydraulic oil storage tank is connected to the intake hole 5 of the housing 2 to connect the hydraulic equipment.
  • the discharged pipe is connected to the discharge hole 6 and a drive motor is connected to the rotary shaft 21 of the drive gear 20 and then the drive gear 20 is rotated by the drive motor.
  • the driven gear 25 meshed with the drive gear 20 rotates, and the hydraulic oil in the hydraulic pressure region sandwiched between the inner peripheral surface 3a of the hydraulic pressure chamber 4, the teeth of the gears 20 and 25, and the side plates 30 and 135 is
  • the gears 20 and 25 are transferred to the discharge hole 6 side by the rotation of the gears 20 and 25, and the entire top part slides on the inner peripheral surface 3a of the hydraulic chamber 4 from the meshing part toward the rotation direction with the meshing part of the gears 20 and 25 as a boundary.
  • the region including the intake hole 5 up to the foremost tooth part in contact is low pressure
  • the region including the discharge hole 6 ahead of the tooth part in the rotational direction is high pressure
  • the hydraulic oil pressurized to high pressure It is sent to the hydraulic equipment through the discharge hole 6 and the piping.
  • each of the rear regions 51 and 56 partitioned into two regions by the partition seals 50 and 55 is the same as the high pressure hydraulic region, with the high pressure regions 51a and 56a communicating with the high pressure hydraulic region, respectively.
  • the other low pressure regions 51b and 56b are communicated with the low pressure hydraulic pressure region and have the same low pressure as the low pressure hydraulic pressure region.
  • FIG. 5 corresponds to FIG. 14 described above, and corresponds to the direction of arrow C in FIG.
  • the gear 20 is illustrated, but the same applies to the gear 25, and the reference numerals related to the gear 25 are given in parentheses.
  • Reference numerals 20 a1 (25 a1 ), 20 a2 (25 a2 ), 20 a3 (25 a3 ), and 20 a4 (25 a4 ) are respectively the top portions (ridge lines ) of the tooth portions.
  • the gear 20 (25) rotates in the direction indicated by the arrow D a (D b ), and in FIG. 5 (a), the top portion located upstream from the sliding contact end CE a (CE b ) indicated by the two-dot chain line.
  • 20 a2 (25 a2 ), 20 a3 (25 a3 ), and 20 a4 (25 a4 ) are in sliding contact with the inner peripheral surface 3 a of the hydraulic chamber 4, while the sliding contact end CE a (CE b ) Exceeding the top portion 20 a1 (25 a1 ), at least a part thereof is not in sliding contact with the inner peripheral surface 3 a. Then, as shown in FIG.
  • the gear 20 (25) rotates in the direction indicated by the arrow D a (D b ), and the top portion 20 a3 (25 a3 ) reaches the sliding contact end CE a (CE b ).
  • the tip portion of the top portion 20 a2 (25 a2 ) in the rotational direction (arrow D a (D b ) direction) exceeds the sliding contact end CE a (CE b ), and the top portion 20 a2 (25 a2 ) and the inner circumference even if the gap between the surface 3a and the side plate 35, the top 20 a2 (25 a2) from the front area (tooth groove between the top 20 a1 and (25 a1) a top 20 a2 (25 a2))
  • the a top portion 20 a2 (25 a2) from the rear area teeth groove between the top 20 a2 and (25 a2) a top 20 a3 (25 a3)
  • the phenomenon that the hydraulic oil flows in from the gap toward the rear region does not occur.
  • the hydraulic pump 100 of this embodiment on its outer teeth in the rotational direction forwardmost in the sliding angle range ⁇ a3 ( ⁇ b3) within exceeds the sliding angle range ⁇ a3 ( ⁇ b3)
  • high-pressure hydraulic fluid flows into the rear region from the rear region 56a through the through hole 135a (135b), and the rear region Therefore, when the foremost tooth portion exceeds the sliding contact end CE a (CE b ) and leaves the inner peripheral surface 3 a of the hydraulic chamber 4, the inner peripheral surface 3 a, the side plate 135, and the gear 20
  • the through holes 135a and 135b are preferably expanded toward the gears 20 and 25. By making the diameter expanded in this way, separation of the flow of hydraulic oil can be suppressed.
  • the helical gears 20 and 25 are respectively connected to the tooth tip and the tooth bottom by arc portions, and are continuously engaged from one end portion to the other end portion in the tooth width direction at the meshing portion.
  • a helical gear (continuous contact wire meshing gear) having a tooth profile on which a contact line is formed is not limited to this, but a helical gear of other tooth profile (including a known general tooth profile) is used. It may be a gear.
  • the positions where the through holes 135a and 135b are provided are positions where the above-described effect is achieved, that is, the tooth part at the forefront in the rotation direction within the sliding contact angle range ⁇ a3 ( ⁇ b3 ) is the sliding contact angle range ⁇ a3.
  • the rear region 56a Before moving to the outside beyond ( ⁇ b3 ), that is, before exceeding the sliding contact end CE a (CE b ), the rear region 56a is connected to the rear region 56a through the through-hole 135a (135b) in the rear region. Any position may be used as long as the hydraulic oil flows in.
  • the inner diameters of the through holes 135a and 135b may be any size as long as the hydraulic oil can circulate, and the size thereof is not limited.
  • the shape of the through holes 135a and 135b is not limited to a round hole, but may be other shapes such as a long hole or a square hole.
  • the rotation direction of the drive gear 20 is clockwise when viewed from the front cover 7 side
  • a right-twisted helical gear is used for the drive gear 20
  • the driven gear 25 is left-twisted.
  • a helical gear is used, the present invention is not limited to this, and a left-twisted helical gear is used as the driving gear by rotating the driving gear 20 in the left direction when viewed from the front cover 7 side.
  • a right-handed helical gear may be used.
  • the hydraulic pump according to the present invention is embodied as a hydraulic pump.
  • the present invention is not limited to this.
  • the hydraulic pump may be embodied as a coolant pump using cutting fluid as a working liquid.

Abstract

A hydraulic device comprises: a pair of helical gears (20, 25); a body (2) for accommodating the gears (20, 25); bearing members (40, 45) for supporting the gears (20, 25); side plates (30, 135) provided between the gears (20, 25) and the bearing members (40, 45); and seal members (50, 55) provided between the side plates (30, 135) and the bearing members (40, 45). The gears (20, 25) are in sliding contact with the inner peripheral surface (3a) of the body (2) in predetermined sliding contact angle ranges. Through-holes are formed in the side plate (135) so as to extend between the front and rear surfaces thereof, the through-holes being located in regions respectively corresponding to the sliding contact angle ranges at positions corresponding to a high-pressure region in a rear surface region (56). A low-pressure region and the high-pressure region in the rear surface region (56) are connected through the through-holes, the low-pressure region being surrounded by the forward-most tooth sections within the sliding contact angle ranges, tooth sections following the forward-most tooth sections, the side plate (135), and the inner peripheral surface (3a).

Description

液圧装置Hydraulic device
　本発明は、歯部が相互に噛み合う一対のはすば歯車を備えた液圧ポンプに関する。 The present invention relates to a hydraulic pump provided with a pair of helical gears whose tooth portions mesh with each other.
　上記液圧ポンプとして、従来、下記特許文献１に開示された液圧ポンプが知られている。図６及び図７に示すように、この液圧ポンプ１は、内部に液圧室４が形成されたハウジング２と、この液圧室４内に配設された一対のはすば歯車であって、それぞれ歯先及び歯底に円弧部が含まれ、噛み合い部で歯幅方向の一方の端部から他方の端部にかけて連続した接触線が形成される歯形を有するはすば歯車、即ち、連続接触線噛合歯車（以下、単に「歯車」という）２０，２５と、一対の軸受部材たるブッシュ４０，４５、及び一対の側板３０，３５とを備える。 Conventionally, a hydraulic pump disclosed in Patent Document 1 below is known as the hydraulic pump. As shown in FIGS. 6 and 7, the hydraulic pump 1 includes a housing 2 in which a hydraulic chamber 4 is formed, and a pair of helical gears disposed in the hydraulic chamber 4. Helical gears each having a tooth shape in which an arc portion is included in the tooth tip and the tooth bottom and a continuous contact line is formed from one end portion to the other end portion in the tooth width direction at the meshing portion, that is, Continuous contact line meshing gears (hereinafter simply referred to as “gears”) 20 and 25, bushes 40 and 45 as a pair of bearing members, and a pair of side plates 30 and 35 are provided.
　前記ハウジング２は、一方の端面から他方の端面に向けて、断面形状がアラビア数字の「８」を模した形状の空間を有する前記液圧室４が形成された本体３と、この本体３の一方端面（前端面）にシール１１を介して液密状に固定されたフロントカバー７と、同様に本体３の他方端面（後端面）にシール１２を介して液密状に固定されたエンドカバー８とから構成され、これら一対のカバー体たるフロントカバー７及びエンドカバー８によって前記液圧室４が閉塞されている。 The housing 2 includes a main body 3 in which the hydraulic chamber 4 having a space whose cross-sectional shape is similar to an Arabic numeral “8” is formed from one end face to the other end face. A front cover 7 fixed to one end face (front end face) via a seal 11 in a liquid-tight manner, and an end cover fixed to the other end face (rear end face) of the main body 3 via a seal 12 in the same manner. The hydraulic chamber 4 is closed by the front cover 7 and the end cover 8 as a pair of cover bodies.
　前記一対の歯車２０，２５は、一方が駆動歯車２０、他方が従動歯車２５である。駆動歯車２０の回転方向をフロントカバー７から見て右回転で使用する場合、駆動歯車２０の歯部は右ねじれとなり、従動歯車２５の歯部は左ねじれとなる。歯車２０は、その両端面からその中心軸に沿ってそれぞれ回転軸２１，２２が延設され、同様に、歯車２５は、その両端面からその中心軸に沿ってそれぞれ回転軸２６，２７が延設されており、これら一対の歯車２０，２５は、相互に噛み合った状態で前記液圧室４内に挿入され、その歯先が前記液圧室４の内周面３ａに摺接するようになっており、前記液圧室４は、この一対の歯車２０，２５の噛み合い部を境に、高圧側と低圧側とに二分される。 One of the pair of gears 20 and 25 is a drive gear 20 and the other is a driven gear 25. When the rotation direction of the drive gear 20 is used in the right direction when viewed from the front cover 7, the teeth of the drive gear 20 are right-handed and the teeth of the driven gear 25 are left-handed. The gear 20 has rotary shafts 21 and 22 extending from its both end surfaces along its central axis. Similarly, the gear 25 has its rotary shafts 26 and 27 extending from its both end surfaces along its central axis. The pair of gears 20 and 25 are inserted into the hydraulic pressure chamber 4 in mesh with each other, and their tooth tips come into sliding contact with the inner peripheral surface 3 a of the hydraulic pressure chamber 4. The hydraulic chamber 4 is divided into a high pressure side and a low pressure side with the meshing portion of the pair of gears 20 and 25 as a boundary.
　また、駆動歯車２０の前方側の回転軸２１の端部２１ａはテーパ状に形成され、更にその先端にはねじ部２１ｂが形成されており、同部は、前記フロントカバー７に形成された貫通孔７ａを通じて外方に延出し、同回転軸２１の外周面と貫通孔７ａの内周面との間がオイルシール１０によってシールされている。尚、この歯車２０，２５の斜視図を図１２に示している。 Further, the end 21a of the rotary shaft 21 on the front side of the drive gear 20 is formed in a taper shape, and further, a screw portion 21b is formed at the tip thereof, and this portion is a through-hole formed in the front cover 7. It extends outward through the hole 7a, and the oil seal 10 seals between the outer peripheral surface of the rotary shaft 21 and the inner peripheral surface of the through hole 7a. A perspective view of the gears 20 and 25 is shown in FIG.
　前記本体３には、その一方の側面に前記液圧室４の低圧側に通じる取入れ穴（取入れ流路）５が形成されるとともに、これと相対する他方の側面に、同じく前記液圧室４の高圧側に通じる吐出し穴（吐出し流路）６が形成されている。そして、これら取入れ穴５及び吐出し穴６は、それぞれの軸線が前記一対の歯車２０，２５間の中心に位置するように設けられている。 The main body 3 is formed with an intake hole (intake channel) 5 that communicates with the low pressure side of the hydraulic pressure chamber 4 on one side surface, and the hydraulic pressure chamber 4 is also formed on the other side surface opposite to this. A discharge hole (discharge flow path) 6 leading to the high pressure side is formed. The intake hole 5 and the discharge hole 6 are provided so that their respective axes are located at the center between the pair of gears 20 and 25.
　図８に示すように、前記側板３０，３５は、アラビア数字の「８」を模した形状に形成された板状の部材からなり、側板３０には、貫通孔３１，３２が形成され、側板３５には、貫通孔３６，３７が形成されている。そして、側板３０は、その貫通孔３１に前記回転軸２１が挿通されるとともに、貫通孔３２に前記回転軸２６が挿通された状態で、歯車２０，２５の前側に配設され、その対向面が歯車２０，２５の歯部を含む前端面全面に当接した状態となっている。一方、側板３５は、その貫通孔３６に前記回転軸２２が挿通されるとともに、貫通孔３７に前記回転軸２７が挿通された状態で、歯車２０，２５の後側に配設され、その対向面が歯車２０，２５の歯部を含む後端面全面に当接した状態となっている。 As shown in FIG. 8, the side plates 30 and 35 are made of plate-like members formed in a shape imitating the Arabic numeral “8”, and the side plates 30 are formed with through holes 31 and 32. Through holes 36 and 37 are formed in 35. The side plate 30 is disposed on the front side of the gears 20 and 25 in a state where the rotary shaft 21 is inserted into the through hole 31 and the rotary shaft 26 is inserted into the through hole 32. Is in contact with the entire front end surface including the teeth of the gears 20 and 25. On the other hand, the side plate 35 is disposed on the rear side of the gears 20 and 25 with the rotary shaft 22 inserted through the through-hole 36 and the rotary shaft 27 inserted through the through-hole 37. The surface is in contact with the entire rear end surface including the teeth of the gears 20 and 25.
　また、側板３０には、前記貫通孔３１，３２の内周面に、表裏に通じる潤滑溝３３，３４が形成され、同様に、側板３５には、前記貫通孔３６，３７の内周面に、表裏に通じる潤滑溝３８，３９が形成されている。前記一対の歯車２０，２５が回転する際に、これら潤滑溝３３，３４，３８，３９を介して、当該歯車２０，２５の端面及び歯底に作動油が導かれ、これにより歯車２０，２５の歯底を冷却することができるとともに、歯車２０，２５と側板３０，３５との間を潤滑して両者の間の摩擦を低減することができるようになっている。 Further, the side plate 30 is formed with lubrication grooves 33 and 34 communicating with the inner and outer surfaces of the through holes 31 and 32, and similarly, the side plate 35 has an inner surface of the through holes 36 and 37. Lubricating grooves 38 and 39 communicating with the front and back sides are formed. When the pair of gears 20 and 25 rotate, the working oil is guided to the end surfaces and the tooth bottoms of the gears 20 and 25 through the lubricating grooves 33, 34, 38 and 39, thereby the gears 20 and 25. Can be cooled, and the gears 20 and 25 and the side plates 30 and 35 can be lubricated to reduce friction between them.
　図９及び図１０に示すように、前記ブッシュ４０，４５は、アラビア数字の「８」を模した形状に形成された軸受であり、ブッシュ４０には、支持穴４１，４２が形成され、同様に、ブッシュ４５には、支持穴４６，４７が形成されている。そして、ブッシュ４０は、その支持穴４１に前記回転軸２１が挿通されるとともに、支持穴４２に前記回転軸２６が挿通された状態で、前記側板３０の前側に配設され、一方、ブッシュ４５は、その支持穴４６に前記回転軸２２が挿通されるとともに、支持穴４７に前記回転軸２７が挿通された状態で、前記側板３５の後側に配設されており、それぞれ、前記回転軸２１，２２，２６，２７を回転自在に支持する。 As shown in FIGS. 9 and 10, the bushes 40 and 45 are bearings formed in a shape imitating the Arabic numeral “8”, and support holes 41 and 42 are formed in the bush 40. In addition, support holes 46 and 47 are formed in the bush 45. The bush 40 is disposed on the front side of the side plate 30 with the rotating shaft 21 inserted through the support hole 41 and the rotating shaft 26 inserted through the support hole 42. Are arranged on the rear side of the side plate 35 in a state where the rotary shaft 22 is inserted into the support hole 46 and the rotary shaft 27 is inserted into the support hole 47, respectively. 21, 22, 26 and 27 are rotatably supported.
　また、ブッシュ４０，４５の、前記側板３０，３５と対向する端面には、アラビア数字の「３」を模した形状のシール溝４０ａ，４５ａが形成されている。そして、図１１に示すように、このシール溝４０ａ，４５ａ内に、それぞれ弾性を有する区画シール５０，５５が配設されている。 Further, seal grooves 40a and 45a having a shape imitating the Arabic numeral “3” are formed on the end surfaces of the bushes 40 and 45 facing the side plates 30 and 35, respectively. As shown in FIG. 11, partition seals 50 and 55 having elasticity are disposed in the seal grooves 40a and 45a, respectively.
　この区画シール５０は、ブッシュ４０と側板３０との間の隙間である背面領域５１を高圧側の領域５１ａと低圧側の領域５１ｂとに区画し、区画シール５５は、ブッシュ４５と側板３５との間の隙間である背面領域５６を高圧側の領域５６ａと低圧側の領域５６ｂとに区画するものである。これら区画シール５０，５５によって区画される背面領域５１，５６の高圧側の領域５１ａ，５６ａには、適宜流路を介して前記液圧室４の高圧側の作動油が導かれるようになっており、前記側板３０，３５は、高圧側の領域５１ａ，５６ａに導かれた高圧の作動油によって、歯車２０，２５の端面にそれぞれ押し付けられ、これにより、各端面を介して、高圧側の作動油が低圧側にリークするのが防止される。 The partition seal 50 partitions a rear region 51, which is a gap between the bush 40 and the side plate 30, into a high pressure side region 51 a and a low pressure side region 51 b, and the partition seal 55 is formed between the bush 45 and the side plate 35. A back surface region 56, which is a gap therebetween, is partitioned into a high pressure side region 56a and a low pressure side region 56b. The hydraulic oil on the high pressure side of the hydraulic pressure chamber 4 is guided to the high pressure side regions 51a and 56a of the back surface regions 51 and 56 partitioned by the partition seals 50 and 55 through an appropriate flow path. The side plates 30 and 35 are pressed against the end surfaces of the gears 20 and 25 by the high-pressure hydraulic oil guided to the high- pressure side regions 51a and 56a, respectively. Oil is prevented from leaking to the low pressure side.
　尚、側板３０，３５には、その歯車２０，２５側の端面にも液圧室４内の高圧の作動油が作用するが、高圧側の空間５１ａ，５６ａ内の受圧面積は、歯車２０，２５側の受圧面積よりも大きくなっており、この結果、側板３０，３５は、その作用力の差によって歯車２０，２５の端面に押し付けられる。 The high pressure hydraulic oil in the hydraulic chamber 4 also acts on the side plates 30 and 35 on the end surfaces of the gears 20 and 25, but the pressure receiving areas in the high pressure spaces 51a and 56a are as follows. As a result, the side plates 30 and 35 are pressed against the end surfaces of the gears 20 and 25 due to the difference in their acting forces.
　また、同図１１に示すように、前記区画シール５０，５５の両端部には、外側に向け折り曲げられ、折り返された折り返し部５０ａ，５５ａが形成されており、これら折り返し部５０ａ，５５ａは、側板３０，３５、液圧室４を構成する本体３の内周面３ａ、及びブッシュ４０，４５（正確にはシール溝４０ａ，４５ａの底面）に液密に当接している。 Further, as shown in FIG. 11, both end portions of the partition seals 50 and 55 are folded outward and folded back portions 50a and 55a. The folded portions 50a and 55a are The side plates 30 and 35, the inner peripheral surface 3a of the main body 3 constituting the hydraulic chamber 4, and the bushes 40 and 45 (more precisely, the bottom surfaces of the seal grooves 40a and 45a) are in liquid-tight contact.
　また、ブッシュ４０の前端面はフロントカバー７の端面に当接し、ブッシュ４５の後端面はエンドカバー８の端面に当接しており、これにより、歯車２０，２５の端面と側板３０，３５とが当接した状態、及び側板３０，３５とブッシュ４０，４５に設けた区画シール５０，５５とがそれぞれ当接した状態となるとともに、これら歯車２０，２５、側板３０，３５、区画シール５０，５５及びブッシュ４０，４５に予圧が付与された状態となっている。そして、区画シール５０，５５は、この与圧によって弾性変形するとともに、その弾発力によって、側板３０，３５及びブッシュ４０，４５に対してそれぞれ液密に当接している。 Further, the front end surface of the bush 40 is in contact with the end surface of the front cover 7, and the rear end surface of the bush 45 is in contact with the end surface of the end cover 8, whereby the end surfaces of the gears 20, 25 and the side plates 30, 35 are connected. The abutting state and the side plates 30, 35 and the partition seals 50, 55 provided on the bushes 40, 45 are in contact with each other, and the gears 20, 25, the side plates 30, 35, the partition seals 50, 55. In addition, a preload is applied to the bushes 40 and 45. The partition seals 50 and 55 are elastically deformed by the applied pressure, and are in liquid-tight contact with the side plates 30 and 35 and the bushes 40 and 45 by the elastic force.
　以上の構成を備えた従来の油圧ポンプ１では、まず、作動油の貯留タンクに接続された配管を前記ハウジング２の取入れ穴５に接続し、油圧機器が接続された配管を前記吐出し穴６に接続するとともに、前記駆動歯車２０の回転軸２１に駆動モータを接続した後、この駆動モータによって駆動歯車２０を回転させる。 In the conventional hydraulic pump 1 having the above configuration, first, the pipe connected to the hydraulic oil storage tank is connected to the intake hole 5 of the housing 2, and the pipe connected to the hydraulic equipment is connected to the discharge hole 6. And a drive motor is connected to the rotary shaft 21 of the drive gear 20, and then the drive gear 20 is rotated by the drive motor.
　これにより、駆動歯車２０に噛み合った従動歯車２５が回転し、前記液圧室４の内周面３ａ、歯車２０，２５の歯部及び側板３０，３５により挟まれた領域の作動油が、歯車２０，２５の回転によって吐出し穴６側に移送され、歯車２０，２５の噛み合い部を境として、吐出し穴６側が高圧側に、取入れ穴５側が低圧側になる。 As a result, the driven gear 25 meshed with the drive gear 20 rotates, and the hydraulic oil in the region sandwiched between the inner peripheral surface 3a of the hydraulic chamber 4, the teeth of the gears 20, 25 and the side plates 30, 35 is transferred to the gear. 20 and 25 are transferred to the discharge hole 6 side, and the discharge hole 6 side becomes the high-pressure side and the intake hole 5 side becomes the low-pressure side with the meshing portion of the gears 20 and 25 as the boundary.
　そして、作動油が吐出し穴６側に移送されることによって取入れ穴５側が負圧になると、タンク内の作動油が配管及び取入れ穴５を介して低圧側の前記液圧室４内に吸引され、前記液圧室４の内周面３ａ、歯車２０，２５の歯部及び側板３０，３５により挟まれた領域の作動油が、歯車２０，２５の回転によって継続的に吐出し穴６側に移送され、高圧に加圧されて吐出し穴６及び配管を介して油圧機器に送られる。 Then, when the hydraulic oil is discharged to the discharge hole 6 side and the intake hole 5 side becomes negative pressure, the hydraulic oil in the tank is sucked into the hydraulic chamber 4 on the low pressure side through the pipe and the intake hole 5. The hydraulic oil in the region sandwiched between the inner peripheral surface 3a of the hydraulic pressure chamber 4, the teeth of the gears 20, 25 and the side plates 30, 35 is continuously discharged by the rotation of the gears 20, 25. , Pressurized to a high pressure, discharged to the hydraulic equipment through the discharge hole 6 and the piping.
国際公開第２０１６／２４５１９号International Publication No. 2016/24519
　ところで、上述した構成の液圧ポンプ１では、前記液圧室４の内周面３ａ、歯車２０，２５の歯部及び側板３０，３５によって囲まれる低圧側の作動油を高い効率で高圧側に移送する、即ち、歯車２０，２５の歯部と液圧室４の内周面３ａとの間で液漏れが極力生じないようにして移送するために、液圧ポンプ１を組み立てた後これを使用する前に、液圧室４の内周面３ａを歯車２０，２５の歯部によって切削（セルフカット）する予備運転が一般的に実施されている。 By the way, in the hydraulic pump 1 having the above-described configuration, the hydraulic oil on the low pressure side surrounded by the inner peripheral surface 3a of the hydraulic chamber 4, the teeth of the gears 20 and 25, and the side plates 30 and 35 is moved to the high pressure side with high efficiency. After the hydraulic pump 1 is assembled, it is transferred in order to transfer, i.e., transfer between the teeth of the gears 20 and 25 and the inner peripheral surface 3a of the hydraulic chamber 4 as much as possible. Before use, a preliminary operation is generally performed in which the inner peripheral surface 3a of the hydraulic chamber 4 is cut (self-cut) by the teeth of the gears 20 and 25.
　組み立て時の油圧ポンプ１は、ブッシュ４０，４５の支持穴４１，４２，４６，４７の各内径が、回転軸２１，２２，２６，２７の各外径よりも所定量だけ大径に仕上げられており、歯車２０，２５が液圧室４の低圧側の内周面３ａに当接可能な状態となっている。したがって、このような油圧ポンプ１を予備運転として上述した使用態様下に置くと、歯車２０，２５が高圧の作動油により低圧側に押されて、その歯先が液圧室４の低圧側の内周面３ａに押圧され、当該低圧側の内周面３ａが歯車２０，２５の歯先によって切削されるのである。そして、歯車２０，２５によって、低圧側に移動可能な量だけ前記内周面３ａが切削されると、当該切削は終了され、歯車２０，２５の歯先が内周面３ａに摺接する状態が実現される。 When assembled, the hydraulic pump 1 is finished such that the inner diameters of the support holes 41, 42, 46, 47 of the bushes 40, 45 are larger than the outer diameters of the rotary shafts 21, 22, 26, 27 by a predetermined amount. Thus, the gears 20 and 25 are in contact with the inner peripheral surface 3 a on the low pressure side of the hydraulic chamber 4. Therefore, when such a hydraulic pump 1 is placed under the above-described use mode as a preliminary operation, the gears 20 and 25 are pushed to the low pressure side by the high pressure hydraulic oil, and the tooth tips thereof are on the low pressure side of the hydraulic chamber 4. The inner peripheral surface 3 a is pressed by the inner peripheral surface 3 a, and the inner peripheral surface 3 a on the low pressure side is cut by the tooth tips of the gears 20 and 25. Then, when the inner peripheral surface 3a is cut by the gears 20, 25 by an amount movable to the low pressure side, the cutting is finished, and the tooth tips of the gears 20, 25 are in sliding contact with the inner peripheral surface 3a. Realized.
　このような予備運転によって、液圧室４の内周面３ａをセルフカットした状態を図１３に示す。尚、この図１３は概略を示すものであって、図６における矢視Ｂ－Ｂ方向の断面図に相当する。 FIG. 13 shows a state in which the inner peripheral surface 3a of the hydraulic chamber 4 is self-cut by such preliminary operation. FIG. 13 shows an outline and corresponds to a cross-sectional view in the direction of arrow BB in FIG.
　図１３に示した例では、歯車２０，２５は略水平方向（矢示Ｅ，Ｆ方向）にそれぞれ押圧されて液圧室４の内周面３ａを切削しており、歯車２０は垂直な基準線ｒから回転方向（矢示Ｄａ方向）に向けて角度θａ１から角度θａ２までの角度範囲（摺接角度範囲）θａ３で内周面３ａに摺接し、角度θａ２を超えた範囲では、歯車２０の歯先は内周面３ａに摺接していない状態となっている。同様に、歯車２５は前記基準線ｒから回転方向（矢示Ｄｂ方向）に向けて角度θｂ１から角度θｂ２までの角度範囲（摺接角度範囲）θｂ３で内周面３ａに摺接し、角度θｂ２を超えた範囲では、歯車２５の歯先は内周面３ａに摺接していない状態となっている。 In the example shown in FIG. 13, the gears 20 and 25 are pressed in a substantially horizontal direction (arrow E and F directions) to cut the inner peripheral surface 3a of the hydraulic chamber 4, and the gear 20 is a vertical reference. Range in which an angle range (sliding contact angle range) from angle θ a1 to angle θ a2 (sliding contact angle range) θ a3 from the line r in the rotation direction (arrow D a direction) exceeds the angle θ a2 Then, the tooth tip of the gear 20 is not in sliding contact with the inner peripheral surface 3a. Similarly, gear 25 is in sliding contact with the inner peripheral surface 3a in an angular range (sliding angle range) theta b3 from the angle theta b1 toward the rotational direction (arrow D b direction) from the reference line r through an angle theta b2 In the range exceeding the angle θb2 , the tooth tip of the gear 25 is not in sliding contact with the inner peripheral surface 3a.
　前記液圧室４の内周面３ａ、歯車２０，２５の歯面及び側板３０，３５によって囲まれる領域（これを「液圧領域」という）の内、前記摺接角度範囲θａ３，θｂ３内にある液圧領域の作動油は低圧ＰＬとなり、摺接角度範囲θａ３，θｂ３を回転方向（矢示Ｄａ，Ｄｂ方向）に超えた範囲の液圧領域の作動油は高圧ＰＨとなる。 The sliding contact angle range θ a3 , θ b3 within the region surrounded by the inner peripheral surface 3 a of the hydraulic chamber 4, the tooth surfaces of the gears 20, 25 and the side plates 30, 35 (referred to as “hydraulic region”). The hydraulic fluid in the hydraulic pressure region in the inside has a low pressure P L , and the hydraulic fluid in the hydraulic pressure region in the range exceeding the sliding contact angle range θ a3 , θ b3 in the rotation direction (arrow D a , D b direction) is high pressure. the P H.
　斯くして、セルフカットを行うことで、液圧室４の低圧側の内周面３ａに歯車２０，２５の歯先を摺接させることができ、このように歯車２０，２５の歯先を液圧室４の内周面３ａに摺接させることで、液圧室４の内周面３ａ、歯車２０，２５の歯部及び側板３０，３５によって囲まれる低圧側の作動油を高い効率で高圧側に移送することが可能となる。 Thus, by performing self-cutting, the tooth tips of the gears 20 and 25 can be brought into sliding contact with the inner peripheral surface 3a on the low pressure side of the hydraulic pressure chamber 4, and thus the tooth tips of the gears 20 and 25 are brought into contact with each other. By making sliding contact with the inner peripheral surface 3a of the hydraulic chamber 4, the low-pressure side hydraulic oil surrounded by the inner peripheral surface 3a of the hydraulic chamber 4, the teeth of the gears 20 and 25, and the side plates 30 and 35 is highly efficient. It can be transferred to the high pressure side.
　ところが、上記のように、液圧室４の低圧側の内周面３ａに歯車２０，２５の歯先を摺接させるようにした従来の油圧ポンプ１では、その摺接の終端部において歯車２０，２５の歯先が液圧室４の内周面３ａから離れるとき、前記内周面３ａ、側板３０，３５及び歯車２０，２５の歯部の相互間に形成される隙間を介して高圧側の作動油が低圧側に流入することになるが、その際、歯車２０，２５がはすば歯車であるので、歯部のねじれによって、前記隙間が徐々に大きくなるという特性を有するため、当初の極僅かな隙間から流入する作動液体は側板３５に向かう噴流となり、この噴流によって側板３５の表面にエロージョン（浸食）が生じるという問題があった。 However, in the conventional hydraulic pump 1 in which the tooth tips of the gears 20 and 25 are slidably contacted with the inner peripheral surface 3a on the low pressure side of the hydraulic chamber 4 as described above, the gear 20 is provided at the end of the sliding contact. When the tooth tips of 25, 25 are separated from the inner peripheral surface 3a of the hydraulic chamber 4, a high-pressure side is provided via a gap formed between the inner peripheral surface 3a, the side plates 30, 35 and the tooth portions of the gears 20, 25. In this case, since the gears 20 and 25 are helical gears, the gap is gradually increased due to the twist of the tooth portion. There is a problem that the working liquid flowing in from a very small gap becomes a jet directed toward the side plate 35, and this jet causes erosion (erosion) on the surface of the side plate 35.
　この問題を、図１４（ａ）～（ｃ）を用いてより詳しく説明する。図１４（ａ）～（ｃ）は、図１２における矢視Ｃ方向の図であり、歯車２０について図示しているが、歯車２５についても同様であるので、当該歯車２５に関係する符号を括弧書きで付している。また、符号２０ａ１（２５ａ１）、２０ａ２（２５ａ２）、２０ａ３（２５ａ３）及び２０ａ４（２５ａ４）はそれぞれ歯部の頂部（稜線）である。 This problem will be described in more detail with reference to FIGS. 14 (a) to (c). 14 (a) to 14 (c) are views in the direction of arrow C in FIG. 12 and illustrate the gear 20, but the same applies to the gear 25. It is attached in writing. Reference numerals 20 a1 (25 a1 ), 20 a2 (25 a2 ), 20 a3 (25 a3 ), and 20 a4 (25 a4 ) are respectively the top portions (ridge lines ) of the tooth portions.
　尚、歯車２０（２５）がはすば歯車の場合、歯すじがねじれているため、前記摺接の終端部において、歯車２０（２５）の歯先が液圧室４の内周面３ａから最初に離れて隙間を生じる部分は、前記歯車２０（２５）の歯すじに沿って各側板３０，３５に向けた方向が歯車２０（２５）の回転方向に対して順方向となる側の側板（この例では側板３５）との間である。 In the case where the gear 20 (25) is a helical gear, the tooth trace is twisted, so that the tooth tip of the gear 20 (25) is separated from the inner peripheral surface 3a of the hydraulic chamber 4 at the end of the sliding contact. The part that first creates a gap is the side plate on the side in which the direction toward the side plates 30 and 35 along the teeth of the gear 20 (25) is the forward direction with respect to the rotation direction of the gear 20 (25). (In this example, the side plate 35).
　図１４において、歯車２０（２５）は矢示Ｄａ（Ｄｂ）方向に回転し、図１４（ａ）では、二点鎖線で示す摺接終端ＣＥａ（ＣＥｂ）より上流側にある頂部２０ａ２（２５ａ２）、２０ａ３（２５ａ３）及び２０ａ４（２５ａ４）は、その全域が液圧室４の内周面３ａに摺接しており、一方、摺接終端ＣＥａ（ＣＥｂ）を超えた頂部２０ａ１（２５ａ１）は少なくともその一部が内周面３ａに摺接していない。斯くして、同図１４（ａ）に示すように、頂部２０ａ１（２５ａ１）と頂部２０ａ２（２５ａ２）との間の作動油は高圧ＰＨ、頂部２０ａ２（２５ａ２）と頂部２０ａ３（２５ａ３）との間の作動油は低圧ＰＬ、頂部２０ａ３（２５ａ３）と頂部２０ａ４（２５ａ４）との間の作動油は低圧ＰＬになっている。 14, the gear 20 (25) rotates in the direction indicated by the arrow D a (D b ), and in FIG. 14 (a), the top portion located upstream from the sliding contact end CE a (CE b ) indicated by a two-dot chain line. 20 a2 (25 a2 ), 20 a3 (25 a3 ), and 20 a4 (25 a4 ) are in sliding contact with the inner peripheral surface 3 a of the hydraulic chamber 4, while the sliding contact end CE a (CE b ) Exceeding the top portion 20 a1 (25 a1 ), at least a part thereof is not in sliding contact with the inner peripheral surface 3 a. Thus, as shown in FIG. 14A, the hydraulic oil between the top 20 a1 (25 a1 ) and the top 20 a2 (25 a2 ) is high pressure P H , the top 20 a2 (25 a2 ) and the top. The hydraulic fluid between 20 a3 (25 a3 ) has a low pressure P L , and the hydraulic fluid between the top 20 a3 (25 a3 ) and the top 20 a4 (25 a4 ) has a low pressure P L.
　次に、図１４（ｂ）に示すように、歯車２０（２５）が矢示Ｄａ（Ｄｂ）方向に回転して、その頂部２０ａ２（２５ａ２）の回転方向（矢示Ｄａ（Ｄｂ）方向）先端部分が摺接終端ＣＥａ（ＣＥｂ）を越えて、この頂部２０ａ２（２５ａ２）と内周面３ａと側板３５との間に隙間を生じると、破線の矢印で示すように、作動油がこの隙間から側板３５に向かう噴流となって頂部２０ａ２（２５ａ２）と頂部２０ａ３（２５ａ３）との間の歯溝に流入する。 Next, as shown in FIG. 14B, the gear 20 (25) rotates in the direction of the arrow D a (D b ), and the rotation direction (arrow D a () of the top 20 a2 (25 a2 ). D b ) direction) When the tip part exceeds the sliding contact end CE a (CE b ) and a gap is formed between the top part 20 a2 (25 a2 ), the inner peripheral surface 3 a and the side plate 35, a broken arrow As shown, the hydraulic oil flows into the tooth gap between the top portion 20 a2 (25 a2 ) and the top portion 20 a3 (25 a3 ) as a jet flow toward the side plate 35 from this gap.
　そして、図１４（ｃ）に示すように、更に、歯車２０（２５）が矢示Ｄａ（Ｄｂ）方向に回転して、頂部２０ａ２（２５ａ２）と内周面３ａと側板３５との間の隙間が大きくなると、頂部２０ａ２（２５ａ２）と頂部２０ａ３（２５ａ３）との間の作動油が高圧ＰＨになる。 Then, as shown in FIG. 14 (c), further, the gear 20 (25) is rotated in the arrow D a (D b) direction, a top 20 a2 (25 a2) and the inner circumferential surface 3a and the side plate 35 When the gap between the larger top portion 20 a2 (25 a2) a top 20 a3 (25 a3) and the hydraulic fluid between the higher pressure P H.
　斯くして、歯車２０（２５）が連続的に矢示Ｄａ（Ｄｂ）方向に回転すると、歯車２０（２５）の各頂部２０ａ（２５ａ）と内周面３ａと側板３５との間に順次繰り返して形成される隙間から、側板３５に向かう噴流が生じ、この繰り返し発生する噴流によって側板３５の表面にエロージョン（浸食）が生じ、このエロージョンによって金属粉が発生するという問題を生じるのである。 Thus, when the gear 20 (25) is continuously rotated in the direction indicated by the arrow D a (D b ), the top 20 a (25 a ), the inner peripheral surface 3 a, and the side plate 35 of the gear 20 (25) A jet flow toward the side plate 35 is generated from the gap formed repeatedly in the middle, and this repeatedly generated jet causes erosion (erosion) on the surface of the side plate 35, which causes a problem that metal powder is generated by this erosion. is there.
　本発明は、以上の実情に鑑みなされたものであって、はすば歯車を用いた液圧ポンプであって、側板にエロージョンが発生するのを効果的に抑制することができる液圧ポンプの提供を、その目的とする。 The present invention has been made in view of the above circumstances, and is a hydraulic pump using a helical gear, which can effectively suppress the occurrence of erosion on the side plate. The purpose is to provide.
　上記課題を解決するための本発明は、
　両端面からそれぞれ外方に延出するように設けられた回転軸を有し、且つ歯部が相互に噛み合う一対のはすば歯車と、
　両端部が開口し、且つ内部に前記一対のはすば歯車が噛み合った状態で収納される液圧室を有し、該液圧室は前記各歯車の外周面に沿った円弧状の内周面を有する本体と、
　前記本体の液圧室内において、前記各歯車の両側に配設され、前記各歯車の回転軸を回転自在に支持する一対の軸受部材と、
　前記一対のはすば歯車と前記一対の軸受部材との間に、前記各はすば歯車の端面に当接するようにそれぞれ配設された一対の側板と、
　前記一対の側板と前記一対の軸受部材との間にそれぞれ配設され、該側板と軸受部材との間に形成される背面領域を２つの領域に区画する弾性を具備したシール部材と、
　前記本体の両端面にそれぞれに液密状に固設されて前記液圧室を封止する一対のカバー体とを備えてなり、
　前記一対のはすば歯車は、その噛み合い部より回転方向側の所定の摺接角度範囲において、それぞれ前記液圧室の内周面に摺接するように構成されるとともに、前記一対の側板、前記一対のはすば歯車の歯面及び前記液圧室の内周面によって囲まれる液圧領域は、前記噛み合い部を境として、この噛み合い部から前記回転方向に向け、頂部全域が前記液圧室の内周面に摺接している最も前方の歯部までの領域が低圧となり、該歯部より回転方向前方の領域が高圧となるように設定され、
　前記シール部材により２つの領域に区画される前記各背面領域は、それぞれその一方の領域が前記高圧の液圧領域に連通されて、その他方の領域よりも高圧に設定され、該一方の領域である高圧領域の範囲が、それぞれ前記摺接角度範囲内に対応した領域にまで及ぶように構成された液圧ポンプにおいて、
　前記はすば歯車に当接する一対の側板の内、前記はすば歯車の歯すじに沿って各側板に向けた方向が前記はすば歯車の回転方向に対して順方向となる側の側板に対し、前記一対のはすば歯車の摺接角度範囲内に対応した各領域内において、前記背面領域の高圧領域に対応する位置に、それぞれ表裏に貫通する貫通孔を穿孔してなり、
　前記摺接角度範囲内において、前記はすば歯車の回転方向の最も前方の歯部、その後続の歯部、前記一対の側板及び前記液圧室の内周面によって囲まれる低圧の領域と、前記背面領域の高圧領域とが、前記貫通孔を介して連通されるように構成された液圧ポンプに係る。 The present invention for solving the above problems is as follows.
A pair of helical gears each having a rotation shaft provided so as to extend outward from both end faces, and the tooth portions mesh with each other;
Both ends have openings, and a hydraulic chamber is housed in a state where the pair of helical gears are engaged with each other, and the hydraulic chamber has an arcuate inner periphery along the outer peripheral surface of each gear. A body having a surface;
A pair of bearing members disposed on both sides of each gear in the hydraulic chamber of the main body and rotatably supporting the rotation shaft of each gear;
A pair of side plates respectively disposed between the pair of helical gears and the pair of bearing members so as to abut against end faces of the helical gears;
A seal member that is provided between the pair of side plates and the pair of bearing members, and has elasticity that partitions a back region formed between the side plates and the bearing member into two regions;
A pair of cover bodies that are fixed in a liquid-tight manner on both end faces of the main body and seal the hydraulic chamber, respectively.
The pair of helical gears are configured to be in sliding contact with the inner peripheral surface of the hydraulic chamber, respectively, in a predetermined sliding contact angle range on the rotational direction side from the meshing portion, and the pair of side plates, The hydraulic pressure region surrounded by the tooth surfaces of the pair of helical gears and the inner peripheral surface of the hydraulic pressure chamber is directed from the meshing portion toward the rotational direction with the meshing portion as a boundary, and the entire top portion is in the hydraulic pressure chamber. The region up to the foremost tooth part that is in sliding contact with the inner peripheral surface of is set to be low pressure, and the region in the rotational direction forward from the tooth part is set to be high pressure,
Each of the back regions divided into two regions by the seal member is set to a higher pressure than the other region, with one of the regions communicating with the high pressure hydraulic region. In a hydraulic pump configured so that a range of a certain high pressure region extends to a region corresponding to each of the sliding contact angle ranges,
Of the pair of side plates in contact with the helical gear, the side plate on the side where the direction toward each side plate along the helical line of the helical gear is the forward direction with respect to the rotational direction of the helical gear. On the other hand, in each region corresponding to the sliding contact angle range of the pair of helical gears, in the position corresponding to the high pressure region of the back surface region, a through hole penetrating the front and back, respectively, is drilled,
Within the sliding contact angle range, the foremost tooth portion in the rotational direction of the helical gear, the subsequent tooth portion, the pair of side plates and the low pressure region surrounded by the inner peripheral surface of the hydraulic pressure chamber, The high pressure area | region of the said back area | region concerns on the hydraulic pump comprised so that it might communicate via the said through-hole.
　上記のように、この液圧ポンプでは、一対のはすば歯車が、その噛み合い部より回転方向側の所定の摺接角度範囲において、それぞれ液圧室の内周面に摺接するように構成されている。そして、一対の側板、一対のはすば歯車の歯面及び液圧室の内周面によって囲まれる液圧領域は、噛み合い部を境として、この噛み合い部から回転方向に向け、頂部全域が液圧室の内周面に摺接している最も前方の歯部までの領域が低圧となり、この歯部より回転方向前方の領域が高圧となる。 As described above, this hydraulic pump is configured such that the pair of helical gears are in sliding contact with the inner peripheral surface of the hydraulic chamber, respectively, within a predetermined sliding contact angle range on the rotational direction side from the meshing portion. ing. The hydraulic region surrounded by the pair of side plates, the tooth surfaces of the pair of helical gears and the inner peripheral surface of the hydraulic chamber is directed from the meshing portion toward the rotation direction with the meshing portion as a boundary, and the entire top portion is liquid. A region to the foremost tooth portion that is in sliding contact with the inner peripheral surface of the pressure chamber has a low pressure, and a region in front of the rotation direction from the tooth portion has a high pressure.
　また、シール部材によりそれぞれ２つの領域に区画される各背面領域は、それぞれ少なくともその一方の領域が高圧の液圧領域に連通されて、前記液圧領域の高圧側と同じ圧力の高圧に設定されており、この一方の領域である高圧領域の範囲は、それぞれ前記摺接角度範囲内に対応した領域にまで及ぶように構成されている。 Each of the back regions divided into two regions by the seal member is set to a high pressure of the same pressure as the high pressure side of the hydraulic pressure region, with at least one of the rear regions communicating with the high pressure hydraulic pressure region. The range of the high pressure region, which is one of the regions, extends to the region corresponding to the sliding contact angle range.
　そして、はすば歯車に当接する一対の側板の内、はすば歯車の歯すじに沿って各側板に向けた方向がはすば歯車の回転方向に対して順方向となる側の側板には、前記一対のはすば歯車の摺接角度範囲内に対応した各領域内において、前記背面領域の高圧領域に対応する位置に、それぞれ表裏に貫通する貫通孔が穿孔され、前記摺接角度範囲内において、はすば歯車の回転方向の最も前方の歯部、その後続の歯部、一対の側板及び液圧室の内周面によって囲まれる低圧の領域と、前記背面領域の高圧領域とが、この貫通孔を介して連通されるように構成されている。 Of the pair of side plates abutting on the helical gear, the side plate along the helical line of the helical gear is directed to each side plate in the forward direction with respect to the rotating direction of the helical gear. In each region corresponding to the sliding contact angle range of the pair of helical gears, through holes penetrating the front and back are respectively drilled at positions corresponding to the high pressure region of the back surface region, and the sliding contact angle Within the range, the foremost tooth portion in the rotation direction of the helical gear, the following tooth portion, the pair of side plates and the low pressure region surrounded by the inner peripheral surface of the hydraulic chamber, and the high pressure region of the back region However, it is comprised so that it may communicate through this through-hole.
　斯くして、この液圧ポンプでは、所定方向に回転するはすば歯車の歯部であって、摺接角度範囲内にある歯部の内、即ち、歯部の頂部全域が液圧室の内周面に摺接している歯部の内、回転方向の最も前方の歯部が、摺接角度範囲を超えてその外側に移動する前に、この最前方の歯部、その後続の歯部、一対の側板及び液圧室の内周面によって囲まれる低圧の領域（後方領域）に、前記貫通孔を介して、背面領域の高圧の作動液体が流入し、この結果、当該後方領域が高圧となる。 Therefore, in this hydraulic pump, the tooth portion of the helical gear that rotates in a predetermined direction, and the tooth portion within the sliding contact angle range, that is, the entire top portion of the tooth portion is the hydraulic chamber. Among the tooth portions that are in sliding contact with the inner peripheral surface, the foremost tooth portion in the rotational direction moves beyond the sliding contact angle range and moves to the outside of the tooth portion. The high-pressure working liquid in the back region flows into the low-pressure region (rear region) surrounded by the pair of side plates and the inner peripheral surface of the hydraulic chamber through the through hole. It becomes.
　このように、前記最前方の歯部が摺接角度範囲を超えてその外側に移動する前に、前記後方領域が高圧となって、当該歯部の前後の領域が同じ高圧となるので、最前方の歯部が摺接角度範囲を超えて、液圧室の内周面から離れるときに、この内周面、側板及びはすば歯車の歯部の相互間に隙間が形成されても、形成された隙間から後方の領域に向けて作動液体が入流するという現象を生じることがなく、このため、側板にエロージョンを生じるという従来の問題は生じない。 Thus, before the foremost tooth part moves beyond the sliding contact angle range, the rear area becomes high pressure, and the areas before and after the tooth part become the same high pressure. When the front tooth part exceeds the sliding contact angle range and leaves the inner peripheral surface of the hydraulic chamber, even if a gap is formed between the inner peripheral surface, the side plate and the helical gear tooth part, There is no occurrence of the phenomenon that the working liquid flows into the rear region from the formed gap, and thus the conventional problem of erosion of the side plate does not occur.
　尚、前記背面領域の高圧の作動液体が、前記貫通孔を介して前記後方領域に向けて流入するが、その流入方向は歯部の歯面に略沿った方向であるので、当該歯部にはエロージョンは生じ難い。 Note that the high-pressure working liquid in the back region flows into the rear region through the through-hole, but the inflow direction is a direction substantially along the tooth surface of the tooth portion. Is unlikely to cause erosion.
　また、前記液圧ポンプにおいて、前記各貫通孔は、前記はすば歯車側に向けて拡径されているのが好ましい。このように拡径形状にすることで、作動液体の流れの剥離を抑制することができる。 Further, in the hydraulic pump, it is preferable that the diameter of each through hole is expanded toward the helical gear side. By making the diameter expanded in this way, separation of the flow of the working liquid can be suppressed.
　以上のように、本発明に係る液圧ポンプでは、はすば歯車の歯部の内、摺接角度範囲内にある最前方の歯部が摺接角度範囲を超えてその外側に出る前に、側板に設けられた貫通孔を通じて、当該歯部の後方領域に背面領域の高圧の作動油が流入して当該後方領域が高圧となり、当該歯部の前後の領域が同じ高圧となるので、最前方の歯部が摺接角度範囲を超えて、液圧室の内周面から離れるときに、この内周面、側板及びはすば歯車の歯部の相互間に隙間が形成されても、形成された隙間から後方領域に向けて作動油が流入するという現象を生じることがなく、このため、側板にエロージョンを生じるという従来の問題を生じない。 As described above, in the hydraulic pump according to the present invention, before the foremost tooth portion within the sliding contact angle range out of the helical gear tooth portion exceeds the sliding contact angle range and goes outside. Since the high-pressure hydraulic fluid in the back region flows into the rear region of the tooth part through the through-hole provided in the side plate, the rear region becomes high pressure, and the regions before and after the tooth part have the same high pressure. When the front tooth part exceeds the sliding contact angle range and leaves the inner peripheral surface of the hydraulic chamber, even if a gap is formed between the inner peripheral surface, the side plate and the helical gear tooth part, The phenomenon that hydraulic oil flows in from the formed gap toward the rear region does not occur, and thus the conventional problem of erosion of the side plate does not occur.
本発明の一実施形態に係る油圧ポンプ示した正断面図である。1 is a front sectional view showing a hydraulic pump according to an embodiment of the present invention. 図１における矢視Ａ’－Ａ’方向の断面図である。FIG. 2 is a cross-sectional view in the direction of arrow A′-A ′ in FIG. 1. 本実施形態に係る側板を示した側面図である。It is the side view which showed the side plate which concerns on this embodiment. 側板に形成する貫通孔の形状を示した説明図である。It is explanatory drawing which showed the shape of the through-hole formed in a side plate. 本実施形態に係る油圧ポンプの作用を説明するための説明図である。It is explanatory drawing for demonstrating the effect | action of the hydraulic pump which concerns on this embodiment. 従来の油圧ポンプ示した正断面図である。It is a front sectional view showing a conventional hydraulic pump. 図６における矢視Ａ－Ａ方向の断面図である。FIG. 7 is a cross-sectional view in the direction of arrow AA in FIG. 6. 図６に示した従来の油圧ポンプの側板を示した側面図である。It is the side view which showed the side plate of the conventional hydraulic pump shown in FIG. 図６に示した従来の油圧ポンプのブッシュを示した正面図である。It is the front view which showed the bush of the conventional hydraulic pump shown in FIG. 図９に示したブッシュの右側面図である。FIG. 10 is a right side view of the bush shown in FIG. 9. 図１０のブッシュに区画シールを装着した状態を示した右側面図である。It is the right view which showed the state which mounted | wore the bush of FIG. 10 with the division seal. 図６に示した従来の油圧ポンプのはすば歯車、側板及びブッシュを示した斜視図である。FIG. 7 is a perspective view showing a helical gear, a side plate, and a bush of the conventional hydraulic pump shown in FIG. 6. 図６における矢視Ｂ－Ｂ方向の断面図である。It is sectional drawing of the arrow BB direction in FIG. 従来の油圧ポンプにおける問題点を説明するための説明図である。It is explanatory drawing for demonstrating the problem in the conventional hydraulic pump.
　以下、本発明の具体的な実施の形態について、図面の図１～図５に基づき説明する。図１は、本発明の一実施形態に係る油圧ポンプを示した正断面図であり、図２は、図１における矢視Ａ’－Ａ’方向の断面図である。また、図３は、本例の油圧ポンプに係る側板を示した側面図であり、図４は、側板に形成する貫通孔の形状を示した説明図であり、図５は、本例の油圧ポンプの作用を説明するための説明図である。 Hereinafter, specific embodiments of the present invention will be described with reference to FIGS. 1 to 5 of the drawings. FIG. 1 is a front sectional view showing a hydraulic pump according to an embodiment of the present invention, and FIG. 2 is a sectional view in the direction of arrow A′-A ′ in FIG. 1. 3 is a side view showing a side plate according to the hydraulic pump of this example, FIG. 4 is an explanatory view showing the shape of a through hole formed in the side plate, and FIG. 5 is a hydraulic diagram of this example. It is explanatory drawing for demonstrating the effect | action of a pump.
　尚、図１～図３に示すように、本例の油圧ポンプ１００は、側板１３５の構成を除いて、図６～図１３に示した従来の油圧ポンプ１と同じ構成を備えている。したがって、図１～図５において、従来の油圧ポンプ１と同じ構成部分については同じ符号を付すとともに、同じ構成部分については上述した説明が適用されるものとし、以下では、その詳しい説明を省略する。また、本例の油圧ポンプ１００においても、従来の油圧ポンプ１と同様に、予備運転によるセルフカットが行われ、歯車２０，２５が液圧室４の内周面３ａに摺接した状態となっている。 Incidentally, as shown in FIGS. 1 to 3, the hydraulic pump 100 of this example has the same configuration as the conventional hydraulic pump 1 shown in FIGS. 6 to 13 except for the configuration of the side plate 135. Accordingly, in FIGS. 1 to 5, the same components as those of the conventional hydraulic pump 1 are denoted by the same reference numerals, and the above description is applied to the same components, and the detailed description thereof will be omitted below. . Also in the hydraulic pump 100 of this example, as in the conventional hydraulic pump 1, self-cutting is performed by preliminary operation, and the gears 20 and 25 are in sliding contact with the inner peripheral surface 3 a of the hydraulic chamber 4. ing.
　上述したように、この油圧ポンプ１００では、前記側板１３５の構成が従来の油圧ポンプ１の側板３５の構成と異なっている。この側板１３５は、図１に示すように、歯車２０，２５の歯すじに沿って当該側板１３５に向けた方向が、歯車２０，２５の回転方向に対して順方向になるものである。一方、側板３０は、歯車２０，２５の歯すじに沿って当該側板３０に向けた方向が、歯車２０，２５の回転方向に対して逆方向になる。 As described above, in the hydraulic pump 100, the configuration of the side plate 135 is different from the configuration of the side plate 35 of the conventional hydraulic pump 1. As shown in FIG. 1, the side plate 135 is such that the direction toward the side plate 135 along the teeth of the gears 20 and 25 is the forward direction with respect to the rotation direction of the gears 20 and 25. On the other hand, the direction of the side plate 30 toward the side plate 30 along the teeth of the gears 20 and 25 is opposite to the rotation direction of the gears 20 and 25.
　図３に側板１３５を図示しているが、この側板１３５は、図８に示した側板３５と同じ外観形状を備えるものであり、側板３５と異なる点は、表裏に貫通する貫通孔１３５ａ，１３５ｂを備えている点のみである。尚、符号１３６，１３７は、上記の貫通孔３６，３７に対応した貫通孔であり、符号１３８，１３９は、上記の潤滑溝３８，３９に対応した潤滑溝である。 Although the side plate 135 is illustrated in FIG. 3, the side plate 135 has the same external shape as the side plate 35 illustrated in FIG. 8, and is different from the side plate 35 in that through holes 135 a and 135 b that penetrate the front and back surfaces. It is only a point provided with. Reference numerals 136 and 137 are through holes corresponding to the through holes 36 and 37, and reference numerals 138 and 139 are lubrication grooves corresponding to the lubricating grooves 38 and 39, respectively.
　前記貫通孔１３５ａは、上述した歯車２０の摺接角度範囲θａ３内に位置するとともに、前記区画シール５５によって区画される背面領域５６の高圧領域５６ａに通じる位置に設けられている。貫通孔１３５ｂも同様に、歯車２５の摺接角度範囲θｂ３内に位置するとともに、前記区画シール５５によって区画される背面領域５６の高圧領域５６ａに通じる位置に設けられる。 The through hole 135a, as well as located in the sliding angle range theta a3 gear 20 described above, is provided at a position leading to the high pressure region 56a of the rear region 56 partitioned by the partition seal 55. Similarly through hole 135b, as well as position the sliding contact angle range θ in b3 gear 25 is provided at a position leading to the high pressure region 56a of the rear region 56 partitioned by the partition seal 55.
　上述した如く、区画シール５５はブッシュ４５と側板１３５との間に形成される背面領域５６を高圧の領域５６ａと低圧の領域５６ｂに区画するシールであって、図３に示すように、この高圧の領域５６ａは、歯車２０の摺接角度範囲θａ３の内側、及び歯車２５の摺接角度範囲θｂ３の内側に対応する領域にまで及んでいる。 As described above, the partition seal 55 is a seal that partitions the back region 56 formed between the bush 45 and the side plate 135 into a high-pressure region 56a and a low-pressure region 56b. As shown in FIG. region 56a of are extend to the inside of the sliding angle range theta a3 gear 20, and a region corresponding to the inside of the sliding angle range theta b3 gear 25.
　尚、図３において、垂直な基準線ｒから角度θａ１となる位置は、歯車２０が液圧室４の内周面３ａに対して摺接を開始する位置であり、基準線ｒから角度θａ２となる位置は、摺接を終了する位置である。同様に、基準線ｒから角度θｂ１となる位置は、歯車２５が液圧室４の内周面３ａに対して摺接を開始する位置であり、基準線ｒから角度θｂ２となる位置は、摺接を終了する位置である。また、ＣＥａは歯車２０が摺接を終了する位置を示し、ＣＥｂは歯車２５が摺接を終了する位置を示している。 In FIG. 3, the position where the angle θ a1 is from the vertical reference line r is the position where the gear 20 starts sliding contact with the inner peripheral surface 3 a of the hydraulic chamber 4 and the angle θ from the reference line r. The position that becomes a2 is a position at which the sliding contact ends. Similarly, the position at the angle θ b1 from the reference line r is the position at which the gear 25 starts sliding contact with the inner peripheral surface 3a of the hydraulic chamber 4, and the position at the angle θ b2 from the reference line r is This is the position where the sliding contact ends. CE a indicates a position where the gear 20 ends sliding contact, and CE b indicates a position where the gear 25 ends sliding contact.
　これら貫通孔１３５ａ，１３５ｂは、図４（ａ）に示すように、一般的には丸穴で良いが、その変形例としては、図４（ｂ）に示すような、歯車２０，２５側に面取りを取った形状（貫通孔１３５ａ’，１３５ｂ’）でも良く、或いは、図４（ｃ）に示すような、歯車２０，２５側に拡径したテーパ形状（貫通孔１３５ａ”，１３５ｂ”）でも良い。 These through- holes 135a and 135b are generally round holes as shown in FIG. 4 (a). However, as a modification, the through- holes 135a and 135b are arranged on the gears 20 and 25 side as shown in FIG. 4 (b). The shape may be chamfered (through holes 135a ′ and 135b ′), or may be a tapered shape (through holes 135a ″ and 135b ″) whose diameter is increased toward the gears 20 and 25 as shown in FIG. good.
　以上の構成を備えた本例の油圧ポンプ１００では、上述した油圧ポンプ１と同様に、まず、作動油の貯留タンクに接続された配管をハウジング２の取入れ穴５に接続し、油圧機器が接続された配管を吐出し穴６に接続するとともに、前記駆動歯車２０の回転軸２１に駆動モータを接続した後、この駆動モータによって駆動歯車２０を回転させる。 In the hydraulic pump 100 of the present example having the above configuration, as in the hydraulic pump 1 described above, first, the pipe connected to the hydraulic oil storage tank is connected to the intake hole 5 of the housing 2 to connect the hydraulic equipment. The discharged pipe is connected to the discharge hole 6 and a drive motor is connected to the rotary shaft 21 of the drive gear 20 and then the drive gear 20 is rotated by the drive motor.
　これにより、駆動歯車２０に噛み合った従動歯車２５が回転し、液圧室４の内周面３ａ、歯車２０，２５の歯部及び側板３０，１３５により挟まれた液圧領域の作動油は、歯車２０，２５の回転によって吐出し穴６側に移送され、歯車２０，２５の噛み合い部を境として、この噛み合い部から回転方向に向け、頂部全域が液圧室４の内周面３ａに摺接している最も前方の歯部までの、取入れ穴５を含む領域が低圧となり、この歯部より回転方向前方の、吐出し穴６を含む領域が高圧となり、高圧に加圧された作動油が吐出し穴６及び配管を介して油圧機器に送られる。 As a result, the driven gear 25 meshed with the drive gear 20 rotates, and the hydraulic oil in the hydraulic pressure region sandwiched between the inner peripheral surface 3a of the hydraulic pressure chamber 4, the teeth of the gears 20 and 25, and the side plates 30 and 135 is The gears 20 and 25 are transferred to the discharge hole 6 side by the rotation of the gears 20 and 25, and the entire top part slides on the inner peripheral surface 3a of the hydraulic chamber 4 from the meshing part toward the rotation direction with the meshing part of the gears 20 and 25 as a boundary. The region including the intake hole 5 up to the foremost tooth part in contact is low pressure, the region including the discharge hole 6 ahead of the tooth part in the rotational direction is high pressure, and the hydraulic oil pressurized to high pressure It is sent to the hydraulic equipment through the discharge hole 6 and the piping.
　また、区画シール５０，５５によってそれぞれ２つの領域に区画される各背面領域５１，５６は、それぞれ高圧の領域５１ａ，５６ａが高圧の液圧領域に連通されて、当該高圧の液圧領域と同じ高圧となり、他方の低圧の領域５１ｂ，５６ｂは低圧の液圧領域に連通されて、当該低圧の液圧領域と同じ低圧となる。 In addition, each of the rear regions 51 and 56 partitioned into two regions by the partition seals 50 and 55 is the same as the high pressure hydraulic region, with the high pressure regions 51a and 56a communicating with the high pressure hydraulic region, respectively. The other low pressure regions 51b and 56b are communicated with the low pressure hydraulic pressure region and have the same low pressure as the low pressure hydraulic pressure region.
　そして、前記貫通孔１３５ａ，１３５ｂが設けられた側板１３５では、作動油がこの貫通孔１３５ａ，１３５ｂを通じて、図５に示すような、挙動を示す。尚、図５は、上述した図１４に対応するものであり、図１２における矢視Ｃ方向に相当する図である。また、図５では、歯車２０について図示しているが、歯車２５についても同様であるので、当該歯車２５に関係する符号を括弧書きで付している。また、符号２０ａ１（２５ａ１）、２０ａ２（２５ａ２）、２０ａ３（２５ａ３）及び２０ａ４（２５ａ４）はそれぞれ歯部の頂部（稜線）である。 In the side plate 135 provided with the through holes 135a and 135b, the hydraulic oil behaves as shown in FIG. 5 through the through holes 135a and 135b. FIG. 5 corresponds to FIG. 14 described above, and corresponds to the direction of arrow C in FIG. In FIG. 5, the gear 20 is illustrated, but the same applies to the gear 25, and the reference numerals related to the gear 25 are given in parentheses. Reference numerals 20 a1 (25 a1 ), 20 a2 (25 a2 ), 20 a3 (25 a3 ), and 20 a4 (25 a4 ) are respectively the top portions (ridge lines ) of the tooth portions.
　図５において、歯車２０（２５）は矢示Ｄａ（Ｄｂ）方向に回転し、図５（ａ）では、二点鎖線で示す摺接終端ＣＥａ（ＣＥｂ）より上流側にある頂部２０ａ２（２５ａ２）、２０ａ３（２５ａ３）及び２０ａ４（２５ａ４）は、その全域が液圧室４の内周面３ａに摺接しており、一方、摺接終端ＣＥａ（ＣＥｂ）を超えた頂部２０ａ１（２５ａ１）は少なくともその一部が内周面３ａに摺接していない。そして、同図５（ａ）に示すように、頂部２０ａ１（２５ａ１）と頂部２０ａ２（２５ａ２）との間の作動油は高圧ＰＨ、頂部２０ａ２（２５ａ２）と頂部２０ａ３（２５ａ３）との間の作動油は高圧ＰＨ、頂部２０ａ３（２５ａ３）と頂部２０ａ４（２５ａ４）との間の作動油は低圧ＰＬとなっている。 In FIG. 5, the gear 20 (25) rotates in the direction indicated by the arrow D a (D b ), and in FIG. 5 (a), the top portion located upstream from the sliding contact end CE a (CE b ) indicated by the two-dot chain line. 20 a2 (25 a2 ), 20 a3 (25 a3 ), and 20 a4 (25 a4 ) are in sliding contact with the inner peripheral surface 3 a of the hydraulic chamber 4, while the sliding contact end CE a (CE b ) Exceeding the top portion 20 a1 (25 a1 ), at least a part thereof is not in sliding contact with the inner peripheral surface 3 a. Then, as shown in FIG. 5 (a), the top 20 a1 (25 a1) a top 20 a2 (25 a2) and the hydraulic fluid between the high pressure P H, the top 20 a2 (25 a2) a top 20 a3 hydraulic oil between (25 a3) is hydraulic oil between the pressure P H, the top 20 a3 (25 a3) a top 20 a4 (25 a4) has a low pressure P L.
　次に、図５（ｂ）に示すように、歯車２０（２５）が矢示Ｄａ（Ｄｂ）方向に回転して、頂部２０ａ３（２５ａ３）が摺接終端ＣＥａ（ＣＥｂ）を超える前に、前記貫通孔１３５ａ（１３５ｂ）が当該頂部２０ａ３（２５ａ３）と頂部２０ａ４（２５ａ４）との間の歯溝に開口し、これらが連通した状態になると、破線の矢印で示すように、高圧の背面領域５６ａの作動油が頂部２０ａ３（２５ａ３）より後方の領域、即ち、頂部２０ａ３（２５ａ３）と頂部２０ａ４（２５ａ４）との間の歯溝に流入し、この結果、図５（ｃ）に示すように、当該歯溝（後方領域）が高圧ＰＨとなる。その際、高圧の背面領域５６ａから前記歯溝（後方領域）に流入する作動油は、その流入方向が当該歯部の歯面に略沿った方向となるので、当該歯部にはエロージョンを生じ難い。 Next, as shown in FIG. 5B, the gear 20 (25) rotates in the direction indicated by the arrow D a (D b ), and the top portion 20 a3 (25 a3 ) reaches the sliding contact end CE a (CE b ). When the through-hole 135a (135b) is opened in the tooth gap between the top 20a3 ( 25a3 ) and the top 20a4 ( 25a4 ) and these are in communication with each other, the broken arrow as shown, the region rearward of the hydraulic oil from the top 20 a3 (25 a3) of the high pressure of the back region 56a, i.e., the tooth groove between the top 20 a3 and (25 a3) a top 20 a4 (25 a4) flowed, as a result, as shown in FIG. 5 (c), the tooth spaces (rear region) becomes the high pressure P H. At that time, the hydraulic oil flowing into the tooth gap (rear region) from the high-pressure back region 56a has an inflow direction substantially along the tooth surface of the tooth portion, so that erosion occurs in the tooth portion. hard.
　一方、頂部２０ａ２（２５ａ２）の回転方向（矢示Ｄａ（Ｄｂ）方向）先端部分が摺接終端ＣＥａ（ＣＥｂ）を越えて、当該頂部２０ａ２（２５ａ２）と内周面３ａと側板３５との間に隙間を生じても、当該頂部２０ａ２（２５ａ２）より前方の領域（頂部２０ａ１（２５ａ１）と頂部２０ａ２（２５ａ２）との間の歯溝）と、当該頂部２０ａ２（２５ａ２）より後方の領域（頂部２０ａ２（２５ａ２）と頂部２０ａ３（２５ａ３）との間の歯溝）とは、既に、同じ高圧となっているので、この隙間から後方の領域に向けて作動油が入流するという現象は生じない。 On the other hand, the tip portion of the top portion 20 a2 (25 a2 ) in the rotational direction (arrow D a (D b ) direction) exceeds the sliding contact end CE a (CE b ), and the top portion 20 a2 (25 a2 ) and the inner circumference even if the gap between the surface 3a and the side plate 35, the top 20 a2 (25 a2) from the front area (tooth groove between the top 20 a1 and (25 a1) a top 20 a2 (25 a2)) When, the a top portion 20 a2 (25 a2) from the rear area (tooth groove between the top 20 a2 and (25 a2) a top 20 a3 (25 a3)), already because have the same pressure, The phenomenon that the hydraulic oil flows in from the gap toward the rear region does not occur.
　このように、本例の油圧ポンプ１００では、摺接角度範囲θａ３（θｂ３）内にある回転方向最前方の歯部が当該摺接角度範囲θａ３（θｂ３）を超えてその外側に移動する前、即ち、前記摺接終端ＣＥａ（ＣＥｂ）を越える前に、その後方の領域に前記貫通孔１３５ａ（１３５ｂ）を通じて背面領域５６ａから高圧の作動油が流入して、当該後方領域が高圧になるので、最前方の歯部が摺接終端ＣＥａ（ＣＥｂ）を越えて、液圧室４の内周面３ａから離れるときに、この内周面３ａ、側板１３５及び歯車２０（２５）の歯部の相互間に隙間が形成されても、形成された隙間から後方の領域に向けて作動油が入流するという現象を生じることがなく、このため、側板にエロージョンを生じるという従来の問題は生じない。 Thus, the hydraulic pump 100 of this embodiment, on its outer teeth in the rotational direction forwardmost in the sliding angle range θ a3 (θ b3) within exceeds the sliding angle range θ a3 (θ b3) Before moving, that is, before exceeding the sliding contact end CE a (CE b ), high-pressure hydraulic fluid flows into the rear region from the rear region 56a through the through hole 135a (135b), and the rear region Therefore, when the foremost tooth portion exceeds the sliding contact end CE a (CE b ) and leaves the inner peripheral surface 3 a of the hydraulic chamber 4, the inner peripheral surface 3 a, the side plate 135, and the gear 20 Even if a gap is formed between the tooth portions of (25), there is no phenomenon that hydraulic oil flows into the rear region from the formed gap, and therefore erosion occurs in the side plate. The conventional problem does not arise.
　尚、この油圧ポンプ１００では、図４（ｂ）及び（ｃ）に示したように、前記各貫通孔１３５ａ，１３５ｂは、歯車２０，２５側に向けて拡径されているのが好ましい。このように拡径形状にすることで、作動油の流れの剥離を抑制することができる。 In the hydraulic pump 100, as shown in FIGS. 4B and 4C, the through holes 135a and 135b are preferably expanded toward the gears 20 and 25. By making the diameter expanded in this way, separation of the flow of hydraulic oil can be suppressed.
　以上、本発明の一実施形態について説明したが、本発明が採り得る具体的な態様は、何らこれに限定されるものではない。 As mentioned above, although one Embodiment of this invention was described, the specific aspect which this invention can take is not limited to this at all.
　例えば、上例の油圧ポンプ１００では、はすば歯車２０，２５を、それぞれ歯先及び歯底に円弧部が含まれ、噛み合い部で歯幅方向の一方の端部から他方の端部にかけて連続した接触線が形成される歯形を有するはすば歯車（連続接触線噛合歯車）としたが、これに限られるものではなく、他の歯形（公知の一般的な歯形を含む）のはすば歯車としても良い。 For example, in the hydraulic pump 100 of the above example, the helical gears 20 and 25 are respectively connected to the tooth tip and the tooth bottom by arc portions, and are continuously engaged from one end portion to the other end portion in the tooth width direction at the meshing portion. A helical gear (continuous contact wire meshing gear) having a tooth profile on which a contact line is formed is not limited to this, but a helical gear of other tooth profile (including a known general tooth profile) is used. It may be a gear.
　また、貫通孔１３５ａ，１３５ｂを設ける位置は、上記効果が奏される位置、即ち、摺接角度範囲θａ３（θｂ３）内にある回転方向最前方の歯部が当該摺接角度範囲θａ３（θｂ３）を超えてその外側に移動する前、即ち、前記摺接終端ＣＥａ（ＣＥｂ）を越える前に、その後方の領域に当該貫通孔１３５ａ（１３５ｂ）を通じて背面領域５６ａから高圧の作動油が流入する位置であれば、どの位置であっても構わない。 Further, the positions where the through holes 135a and 135b are provided are positions where the above-described effect is achieved, that is, the tooth part at the forefront in the rotation direction within the sliding contact angle range θ a3 (θ b3 ) is the sliding contact angle range θ a3. Before moving to the outside beyond (θ b3 ), that is, before exceeding the sliding contact end CE a (CE b ), the rear region 56a is connected to the rear region 56a through the through-hole 135a (135b) in the rear region. Any position may be used as long as the hydraulic oil flows in.
　また、貫通孔１３５ａ，１３５ｂの内径は、作動油が流通できる大きさであれば良く、その大小に制限はない。 Further, the inner diameters of the through holes 135a and 135b may be any size as long as the hydraulic oil can circulate, and the size thereof is not limited.
　また、貫通孔１３５ａ，１３５ｂの形状は、丸穴に限らず、長穴や角穴などの他の形状であっても良い。 The shape of the through holes 135a and 135b is not limited to a round hole, but may be other shapes such as a long hole or a square hole.
　また、上例の油圧ポンプ１００においては、駆動歯車２０の回転方向をフロントカバー７側から見て右回転として、駆動歯車２０に右ねじれのはすば歯車を用い、従動歯車２５に左ねじれのはすば歯車を用いたが、これに限られるものではなく、駆動歯車２０の回転方向をフロントカバー７側から見て左回転として、駆動歯車に左ねじれのはすば歯車を用い、従動歯車に右ねじれのはすば歯車を用いるようにしても良い。 In the hydraulic pump 100 of the above example, the rotation direction of the drive gear 20 is clockwise when viewed from the front cover 7 side, a right-twisted helical gear is used for the drive gear 20, and the driven gear 25 is left-twisted. Although a helical gear is used, the present invention is not limited to this, and a left-twisted helical gear is used as the driving gear by rotating the driving gear 20 in the left direction when viewed from the front cover 7 side. Alternatively, a right-handed helical gear may be used.
　更に、上例では、本発明に係る液圧ポンプを油圧ポンプとして具現化したが、これに限られるものではなく、例えば、切削液を作動液体とするクーラントポンプとして具現化しても良い。 Furthermore, in the above example, the hydraulic pump according to the present invention is embodied as a hydraulic pump. However, the present invention is not limited to this. For example, the hydraulic pump may be embodied as a coolant pump using cutting fluid as a working liquid.
　１　　油圧ポンプ
　２　　ハウジング
　３　　本体
　３ａ　内周面
　４　　液圧室
　７　　フロントカバー
　８　　エンドカバー
　２０，２５　（はすば）歯車
　２１，２２，２６，２７　回転軸
　３０，３５　側板
　４０，４５　ブッシュ
　４０ａ，４５ａ　シール溝
　５０，５５　区画シール
　１００　油圧ポンプ
　１３５　側板
　１３５ａ，１３５ｂ　貫通孔
　θａ３，θｂ３　摺接角度範囲
  DESCRIPTION OF SYMBOLS 1 Hydraulic pump 2 Housing 3 Main body 3a Inner peripheral surface 4 Hydraulic chamber 7 Front cover 8 End cover 20, 25 (Helix) Gear 21, 22, 26, 27 Rotating shaft 30, 35 Side plate 40, 45 Bush 40a, 45a seal groove 50, 55 partition seal 100 hydraulic pump 135 side plate 135a, 135b through holes theta a3, theta b3 sliding angle range

Claims (2)

  1. 　両端面からそれぞれ外方に延出するように設けられた回転軸を有し、且つ歯部が相互に噛み合う一対のはすば歯車と、
    　両端部が開口し、且つ内部に前記一対のはすば歯車が噛み合った状態で収納される液圧室を有し、該液圧室は前記各歯車の外周面に沿った円弧状の内周面を有する本体と、
    　前記本体の液圧室内において、前記各歯車の両側に配設され、前記各歯車の回転軸を回転自在に支持する一対の軸受部材と、
    　前記一対のはすば歯車と前記一対の軸受部材との間に、前記各はすば歯車の端面に当接するようにそれぞれ配設された一対の側板と、
    　前記一対の側板と前記一対の軸受部材との間にそれぞれ配設され、該側板と軸受部材との間に形成される背面領域を２つの領域に区画する弾性を具備したシール部材と、
    　前記本体の両端面にそれぞれに液密状に固設されて前記液圧室を封止する一対のカバー体とを備えてなり、
    　前記一対のはすば歯車は、その噛み合い部より回転方向側の所定の摺接角度範囲において、それぞれ前記液圧室の内周面に摺接するように構成されるとともに、前記一対の側板、前記一対のはすば歯車の歯面及び前記液圧室の内周面によって囲まれる液圧領域は、前記噛み合い部を境として、この噛み合い部から前記回転方向に向け、頂部全域が前記液圧室の内周面に摺接している最も前方の歯部までの領域が低圧となり、該歯部より回転方向前方の領域が高圧となるように設定され、
    　前記シール部材により２つの領域に区画される前記各背面領域は、それぞれその一方の領域が前記高圧の液圧領域に連通されて、その他方の領域よりも高圧に設定され、該一方の領域である高圧領域の範囲が、それぞれ前記摺接角度範囲内に対応した領域にまで及ぶように構成された液圧ポンプにおいて、
    　前記はすば歯車に当接する一対の側板の内、前記はすば歯車の歯すじに沿って各側板に向けた方向が前記はすば歯車の回転方向に対して順方向となる側の側板に対し、前記一対のはすば歯車の摺接角度範囲内に対応した各領域内において、前記背面領域の高圧領域に対応する位置に、それぞれ表裏に貫通する貫通孔を穿孔してなり、
    　前記摺接角度範囲内において、前記はすば歯車の回転方向の最も前方の歯部、その後続の歯部、前記一対の側板及び前記液圧室の内周面によって囲まれる低圧の領域と、前記背面領域の高圧領域とが、前記貫通孔を介して連通されるように構成されていることを特徴とする液圧ポンプ。     A pair of helical gears each having a rotation shaft provided so as to extend outward from both end faces, and the tooth portions mesh with each other;
    Both ends have openings, and a hydraulic chamber is housed in a state where the pair of helical gears are engaged with each other, and the hydraulic chamber has an arcuate inner periphery along the outer peripheral surface of each gear. A body having a surface;
    A pair of bearing members disposed on both sides of each gear in the hydraulic chamber of the main body and rotatably supporting the rotation shaft of each gear;
    A pair of side plates respectively disposed between the pair of helical gears and the pair of bearing members so as to abut against end faces of the helical gears;
    A seal member that is provided between the pair of side plates and the pair of bearing members, and has elasticity that partitions a back region formed between the side plates and the bearing member into two regions;
    A pair of cover bodies that are fixed in a liquid-tight manner on both end faces of the main body and seal the hydraulic chamber, respectively.
    The pair of helical gears are configured to be in sliding contact with the inner peripheral surface of the hydraulic chamber, respectively, in a predetermined sliding contact angle range on the rotational direction side from the meshing portion, and the pair of side plates, The hydraulic pressure region surrounded by the tooth surfaces of the pair of helical gears and the inner peripheral surface of the hydraulic pressure chamber is directed from the meshing portion toward the rotational direction with the meshing portion as a boundary, and the entire top portion is in the hydraulic pressure chamber. The region up to the foremost tooth part that is in sliding contact with the inner peripheral surface of is set to be low pressure, and the region in the rotational direction forward from the tooth part is set to be high pressure,
    Each of the back regions divided into two regions by the seal member is set to a higher pressure than the other region, with one of the regions communicating with the high pressure hydraulic region. In a hydraulic pump configured so that a range of a certain high pressure region extends to a region corresponding to each of the sliding contact angle ranges,
    Of the pair of side plates in contact with the helical gear, the side plate on the side where the direction toward each side plate along the helical line of the helical gear is the forward direction with respect to the rotational direction of the helical gear. On the other hand, in each region corresponding to the sliding contact angle range of the pair of helical gears, in the position corresponding to the high pressure region of the back surface region, a through hole penetrating the front and back, respectively, is drilled,
    Within the sliding contact angle range, the foremost tooth portion in the rotational direction of the helical gear, the subsequent tooth portion, the pair of side plates and the low pressure region surrounded by the inner peripheral surface of the hydraulic pressure chamber, A hydraulic pump, characterized in that the high-pressure region in the back region is configured to communicate with the through-hole.
  2. 　前記各貫通孔は、前記はすば歯車側に向けて拡径されていることを特徴とする請求項１記載の液圧ポンプ。
          The hydraulic pump according to claim 1, wherein each through hole has a diameter increased toward the helical gear side.
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