CN108291539B - Hydraulic device - Google Patents
Hydraulic device Download PDFInfo
- Publication number
- CN108291539B CN108291539B CN201780003969.6A CN201780003969A CN108291539B CN 108291539 B CN108291539 B CN 108291539B CN 201780003969 A CN201780003969 A CN 201780003969A CN 108291539 B CN108291539 B CN 108291539B
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- China
- Prior art keywords
- gear
- pair
- side plate
- sliding contact
- helical gear
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- 230000002093 peripheral effect Effects 0.000 claims abstract description 68
- 239000000203 mixture Substances 0.000 claims description 9
- 239000007788 liquid Substances 0.000 claims description 7
- 230000000149 penetrating effect Effects 0.000 abstract 1
- 238000007789 sealing Methods 0.000 description 18
- 238000005260 corrosion Methods 0.000 description 7
- 230000007797 corrosion Effects 0.000 description 7
- 210000003781 tooth socket Anatomy 0.000 description 7
- 239000012530 fluid Substances 0.000 description 6
- 238000010586 diagram Methods 0.000 description 5
- 238000005461 lubrication Methods 0.000 description 5
- 230000000694 effects Effects 0.000 description 4
- 230000008030 elimination Effects 0.000 description 4
- 238000003379 elimination reaction Methods 0.000 description 4
- 238000003776 cleavage reaction Methods 0.000 description 3
- 230000007017 scission Effects 0.000 description 3
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 238000001816 cooling Methods 0.000 description 2
- 230000003628 erosive effect Effects 0.000 description 2
- 238000011144 upstream manufacturing Methods 0.000 description 2
- 238000005452 bending Methods 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- CUZMQPZYCDIHQL-VCTVXEGHSA-L calcium;(2s)-1-[(2s)-3-[(2r)-2-(cyclohexanecarbonylamino)propanoyl]sulfanyl-2-methylpropanoyl]pyrrolidine-2-carboxylate Chemical group [Ca+2].N([C@H](C)C(=O)SC[C@@H](C)C(=O)N1[C@@H](CCC1)C([O-])=O)C(=O)C1CCCCC1.N([C@H](C)C(=O)SC[C@@H](C)C(=O)N1[C@@H](CCC1)C([O-])=O)C(=O)C1CCCCC1 CUZMQPZYCDIHQL-VCTVXEGHSA-L 0.000 description 1
- 239000002173 cutting fluid Substances 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- PCHJSUWPFVWCPO-UHFFFAOYSA-N gold Chemical compound [Au] PCHJSUWPFVWCPO-UHFFFAOYSA-N 0.000 description 1
- 239000010931 gold Substances 0.000 description 1
- 229910052737 gold Inorganic materials 0.000 description 1
- 230000008676 import Effects 0.000 description 1
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- 239000000843 powder Substances 0.000 description 1
- 238000007493 shaping process Methods 0.000 description 1
- 238000005507 spraying Methods 0.000 description 1
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
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
Abstract
Hydraulic device of the invention has: a pair of of helical gear (20,25)；Ontology (2) is stored gear (20,25)；Parts of bearings (40,45) supports gear (20,25)；Side plate (30,135) is arranged between gear (20,25) and parts of bearings (40,45)；And seal member (50,55), it is arranged between side plate (30,135) and parts of bearings (40,45).Gear (20,25) in specific sliding contact angular range with inner peripheral surface (3a) sliding contact of ontology (2).To side plate (135), and sliding contact angular range in corresponding each region position corresponding with the high-pressure area of rear surface regions (56), wear the through hole for penetrating into front and the back side respectively.It is connected to the high-pressure area of rear surface regions (56) via through hole by the area of low pressure that the teeth portion of the forefront in sliding contact angular range, its subsequent teeth portion, side plate (135) and inner peripheral surface (3a) surround.
Description
Technical field
The present invention relates to a kind of hydraulic pumps for having intermeshing a pair of of the helical gear of teeth portion.
Background technique
As the hydraulic pump, conventionally, there is known the hydraulic pump disclosed in following patent documents 1.Such as Fig. 6 and Fig. 7 institute
Show, which has: shell 2 forms hydraulic pressure chamber 4 in inside；Helical gear namely continuously contacts with line meshing gear
(hreinafter referred to as " gear ") 20,25, it is a pair of of the helical gear being disposed in the hydraulic pressure chamber 4, and has such as lower toothed,
That is, including respectively arc sections in tooth top and bottom of the tooth, formed in engaging section from an end to another end in tooth width direction
Continuous contact line；Bushing 40,45 as a pair of bearings component；And a pair of side plates 30,35.
The shell 2 includes: ontology 3, forms the hydraulic pressure chamber 4, the liquid from an end face towards another end face
Pressure chamber 4 has the space of the shape of cross sectional shape imitation Arabic numerals " 8 "；Front cover 7 is fixed via sealing element 11 in the close shape of liquid
In an end face (front end face) of the ontology 3；And end cap 8, similarly ontology 3 is fixed in the close shape of liquid via sealing element 12
Another end face (rear end face)；The hydraulic pressure chamber 4 is blocked by these front covers 7 and end cap 8 as a pair of of lid.
In the pair of gear 20,25, one of them is driving gear 20, another is driven gear 25.Make to drive
In the case where transferring use when the direction of rotation of gear 20 is from front cover 7 for dextrorotation, the teeth portion of driving gear 20 becomes right torsion
Turn, the teeth portion of driven gear 25 becomes left handed twist.Gear 20, which is each extended over from its both ends of the surface along its central axis, to be arranged
Rotary shaft 21,22, similarly, gear 25, which is each extended over from its both ends of the surface along its central axis, is arranged rotary shaft 26,27,
This pair of of gear 20,25 is inserted into the hydraulic pressure chamber 4 with intermeshing state, their tooth top and the hydraulic pressure chamber 4
Inner peripheral surface 3a sliding contact, the hydraulic pressure chamber 4 using the engaging section of a pair of gear 20,25 as boundary, be divided into high-pressure side with it is low
Press the part of side two.
In addition, the end 21a of the rotary shaft 21 of the front side of driving gear 20 is formed as cone-shaped, and then in end 21a
Front end form screw division 21b, which is extended outward and being formed in the through hole 7a of the front cover 7, the rotary shaft
It is sealed between 21 outer peripheral surface and the inner peripheral surface of through hole 7a by oil sealing 10.In addition, indicating the vertical of the gear 20,25 in Figure 12
Body figure.
In the ontology 3, (stream is taken into the hole that is taken into that its side forms the low-pressure side for leading to the hydraulic pressure chamber 4
Road) 5, and in another side opposite with hole (being taken into flow path) 5 is taken into, it is identically formed and leads to the hydraulic pressure chamber 4
On high-tension side squit hole (spraying flow path) 6.Moreover, these, which are taken into hole 5 and squit hole 6, is located at the pair of tooth with respective axis
The mode at the center between wheel 20,25 is arranged.
As shown in figure 8, the side plate 30,35 is made of the plate-shaped member for being formed as imitating the shape of Arabic numerals " 8 ",
Through hole 31,32 is formed in side plate 30, forms through hole 36,37 in side plate 35.Moreover, side plate 30 is in its perforation
Hole 31 inserts the rotary shaft 21 and inserts the state of the rotary shaft 26 in through hole 32, is disposed in gear 20,25
Front side, and become the state that its opposite surface is connected to the entire front end face including the teeth portion comprising gear 20,25.Another party
Face, side plate 35 are to insert the rotary shaft 22 with the through hole 36 at it and insert the rotary shaft 27 in through hole 37
State, be disposed in the rear side of gear 20,25, and the opposite surface for becoming it is connected to including the teeth portion comprising gear 20,25
The state of entire rear end face.
In addition, forming the lubrication groove for leading to front and the back side in the inner peripheral surface of the through hole 31,32 in side plate 30
33,34, similarly, in side plate 35, the lubrication groove for leading to front and the back side is formed in the inner peripheral surface of the through hole 36,37
38,39.When the rotation of the pair of gear 20,25, working oil is oriented to the gear via these lubrication grooves 33,34,38,39
20,25 end face and bottom of the tooth, thus, it is possible to which the bottom of the tooth of gear 20,25 is cooling, and can by gear 20,25 and side plate 30,
It is lubricated between 35 and reduces friction between the two.
As shown in FIG. 9 and 10, the bushing 40,45 is created as imitating the bearing of the shape of Arabic numerals " 8 ",
Bushing 40 forms supported hole 41,42, similarly, forms supported hole 46,47 in bushing 45.Moreover, bushing 40 is at it
Supported hole 41 insert the rotary shaft 21 and insert the state of the rotary shaft 26 in supported hole 42, be disposed in described
The front side of side plate 30, on the other hand, bushing 45 is the rotary shaft 22 to be inserted with the supported hole 46 at it and in supported hole
47 insert the state of the rotary shaft 27, are disposed in the rear side of the side plate 35, respectively by the rotary shaft 21,22,26,27
It is freely and rotatably supported.
In addition, forming imitation Arabic numerals " 3 " in the end face with 30,35 opposite direction of side plate of bushing 40,45
Seal groove 40a, 45a of shape.Moreover, as shown in figure 11, in the seal groove 40a, 45a, being separately equipped with flexible
Divide sealing element 50,55.
Rear surface regions 51 as the gap between bushing 40 and side plate 30 are divided into high-pressure side by the division sealing element 50
Region 51a and low-pressure side region 51b, divide sealing element 55 for the back panel as the gap between bushing 45 and side plate 35
Domain 56 is divided into the region 56b of on high-tension side region 56a and low-pressure side.The back side that sealing element 50,55 divides is divided to by these
High pressure side region 51a, 56a in region 51,56 suitably imports the on high-tension side working oil of the hydraulic pressure chamber 4, institute via flow path
The end face that side plate 30,35 is pressed against gear 20,25 by the working oil for being directed to the high pressure of high pressure side region 51a, 56a respectively is stated,
Prevent on high-tension side working oil from leaking via each end face to low-pressure side as a result,.
In addition, in side plate 30,35, although the working oil of the high pressure in hydraulic pressure chamber 4 acts also on their gear 20,25 sides
End face, but the compression area on high-tension side space 51a, 56a be greater than gear 20,25 sides compression area, as a result, side
Plate 30,35 is pressed against the end face of gear 20,25 because of the difference of the active force.
In addition, as shown in Fig. 11, at the both ends for dividing sealing element 50,55, being formed towards outside bending simultaneously
Revers turn part 50a, 55a of inflection, these revers turn parts 50a, 55a be connected in liquid-tight manner side plate 30,35, constitute the ontology 3 of hydraulic pressure chamber 4
Inner peripheral surface 3a and bushing 40,45 (being the bottom surface of seal groove 40a, 45a for accurate).
In addition, the front end face of bushing 40 is connected to the end face of front cover 7, the rear end face of bushing 45 is connected to the end face of end cap 8,
As a result, as the state that is abutted with side plate 30,35 of end face of gear 20,25 and side plate 30,35 with bushing 40,45 is set
Divide the state that abuts respectively of sealing element 50,55, and become to these gears 20,25, side plate 30,35, divide sealing element 50,
55 and bushing 40,45 impart the state of precompressed.Moreover, dividing the utilization precompressed of sealing element 50,55 and flexible deformation, and benefit
With its elastic force, and abutted in liquid-tight manner respectively relative to side plate 30,35 and bushing 40,45.
In the previous oil pressure pump 1 for having the above composition, firstly, the piping for the hold-up tank for being connected to working oil is connected
It is taken into hole 5 in the shell 2, the piping that will be connected to oil pressure unit is connected to the squit hole 6, and drive motor is connected
It connects after the rotary shaft 21 of the driving gear 20, makes that gear 20 is driven to rotate using the drive motor.
The driven gear 25 engaged as a result, with driving gear 20 rotates, thus by inner peripheral surface 3a, the tooth of the hydraulic pressure chamber 4
The working oil in the region that the teeth portion and side plate 30,35 of wheel 20,25 clip is transferred by the rotation of gear 20,25 to 6 side of squit hole,
Using the engaging section of gear 20,25 as boundary, 6 side of squit hole becomes high-pressure side, is taken into 5 side of hole as low-pressure side.
Moreover, if the work for making to be taken into 5 side of hole as negative pressure, in slot to the transfer of 6 side of squit hole by working oil
Make oil can be sucked into the hydraulic pressure chamber 4 of low-pressure side via being piped and being taken into hole 5, by the inner peripheral surface 3a of the hydraulic pressure chamber 4,
The working oil in the region that the teeth portion and side plate 30,35 of gear 20,25 clip is continued by the rotation of gear 20,25 to squit hole
The transfer of 6 sides is passed through from squit hole 6 after being pressurised into high pressure and is piped to oil pressure unit conveying.
Background technology document
Patent document
Patent document 1: International Publication No. 2016/24519
Summary of the invention
[problems to be solved by the invention]
And say, in the hydraulic pump 1 of the composition, in order to will be by the inner peripheral surface 3a of the hydraulic pressure chamber 4, gear 20,25
The working oil for the low-pressure side that teeth portion and side plate 30,35 surround is transferred with higher efficiency to high-pressure side, that is to say, that in order in tooth
It is transferred in a manner of not generating leakage as far as possible between the teeth portion of wheel 20,25 and the inner peripheral surface 3a of hydraulic pressure chamber 4, and by hydraulic pump 1
After assembling and using before it, general implementation cuts the inner peripheral surface 3a of hydraulic pressure chamber 4 (certainly using the teeth portion of gear 20,25
Cutting) elimination run.
Oil pressure pump 1 when assembled becomes following state: each internal diameter of the supported hole 41,42,46,47 of bushing 40,45 is smart
It is processed as each outer diameter only big specific quantity than rotary shaft 21,22,26,27, and gear 20,25 can be connected to the low of hydraulic pressure chamber 4
Press the inner peripheral surface 3a of side.Therefore, if making this 1 elimination run of oil pressure pump and being placed under the use form, gear 20,
25 can be by the operating oil pressure of high pressure to low-pressure side, their tooth top is pressed against the inner peripheral surface 3a of the low-pressure side of hydraulic pressure chamber 4, thus
The inner peripheral surface 3a of the low-pressure side is cut by the tooth top of gear 20,25.Moreover, if using gear 20,25 by the inner peripheral surface 3a
Cutting then the cutting terminates, and can realize the tooth top of gear 20,25 and inner peripheral surface 3a sliding and connect to the amount of low-pressure side movement
The state of touching.
The state for carrying out Self cleavage to the inner peripheral surface 3a of hydraulic pressure chamber 4 by this elimination run is indicated in Figure 13.In addition, should
Figure 13 is the figure for indicating outline, is equivalent to the cross-sectional view in the arrow view direction B-B in Fig. 6.
In the example shown in Figure 13, gear 20,25 is pressed respectively and cuts in a generally horizontal direction (direction arrow E, F)
Cut the inner peripheral surface 3a of hydraulic pressure chamber 4, gear 20 becomes following state: from vertical reference line r towards direction of rotation (arrow DaSide
To) with angle, θa1To angle, θa2Angular range (sliding contact angular range) θa3It is being more than angle with inner peripheral surface 3a sliding contact
Spend θa2In the range of, the tooth top of gear 20 not with inner peripheral surface 3a sliding contact.Similarly, gear 25 becomes following state: from institute
Reference line r is stated towards direction of rotation (arrow DbDirection) with angle, θb1To angle, θb2Angular range (sliding contact angular range)
θb3It is being more than angle, θ with inner peripheral surface 3a sliding contactb2In the range of, the tooth top of gear 25 not with inner peripheral surface 3a sliding contact.
The region surrounded by the inner peripheral surface 3a of the hydraulic pressure chamber 4, the flank of tooth of gear 20,25 and side plate 30,35 is (by the region
Referred to as " hydraulic area ") it is interior in the sliding contact angular range, thetaa3、θb3The working oil of interior hydraulic area becomes low pressure PL,
In direction of rotation (arrow Da、DbDirection) on be more than sliding contact angular range, thetaa3、θb3Range hydraulic area working oil
As high pressure PH。
In this way, the inner peripheral surface 3a of the tooth top of gear 20,25 and the low-pressure side of hydraulic pressure chamber 4 can be made by carrying out Self cleavage
Sliding contact can will be by hydraulic by making the tooth top of gear 20,25 and the inner peripheral surface 3a sliding contact of hydraulic pressure chamber 4 like this
The working oil for the low-pressure side that the inner peripheral surface 3a of room 4, the teeth portion of gear 20,25 and side plate 30,35 surround is with higher efficiency to height
Press side transfer.
However, as described above, the inner peripheral surface 3a sliding contact of the low-pressure side in the tooth top and hydraulic pressure chamber 4 for making gear 20,25
Previous oil pressure pump 1 in, when the tooth top of the terminal part gear 20,25 in their sliding contacts is from the inner peripheral surface 3a of hydraulic pressure chamber 4
When leaving, on high-tension side working oil can through the formation of the inner peripheral surface 3a, side plate 30,35 and gear 20,25 teeth portion it is mutual
Between gap and to low-pressure side flow into, at this point, due to gear 20,25 be helical gear, so have due to the torsion of teeth portion
The characteristic that the gap becomes larger, therefore there are the following problems: the working fluid that the atomic small gap from originally flows at
Towards the jet flow of side plate 35, to cause to generate corrosion (erosion) on the surface of side plate 35 because of the jet flow.
The problem is described in more detail using Figure 14 (a)~(c).Figure 14 (a)~(c) is the arrow view direction C in Figure 12
Figure, gear 20 is shown, but also identical about gear 25, so will symbol relevant to the gear 25 with parantheses mark
Note.In addition, symbol 20a1(25a1)、20a2(25a2)、20a3(25a3) and 20a4(25a4) be respectively teeth portion top (crest line).
In addition, in the case where gear 20 (25) is helical gear, since tooth trace reverses, so in the sliding contact
The tooth top of terminal part, gear 20 (25) initially moved away from from the inner peripheral surface 3a of hydraulic pressure chamber 4 and generate the part in gap for along institute
Stating direction of rotation of the tooth trace of gear 20 (25) towards the direction of each side plate 30,35 relative to gear 20 (25) becomes positive one
Between the side plate (being in this embodiment side plate 35) of side.
In Figure 14, gear 20 (25) is to arrow Da(Db) direction rotates, in Figure 14 (a), in than by two o'clock chain line institute
The sliding contact terminal CE showna(CEb) top 20 on the upstream sidea2(25a2)、20a3(25a3) and 20a4(25a4) universe and liquid
On the other hand the inner peripheral surface 3a sliding contact of pressure chamber 4 is more than sliding contact terminal CEa(CEb) top 20a1(25a1) at least it
A part not with inner peripheral surface 3a sliding contact.In this way, as shown in the Figure 14 (a), top 20a1(25a1) and top 20a2(25a2)
Between working oil become high pressure PH, top 20a2(25a2) and top 20a3(25a3) between working oil become low pressure PL, top
20a3(25a3) and top 20a4(25a4) between working oil become low pressure PL。
Secondly, as shown in Figure 14 (b), if gear 20 (25) is to arrow Da(Db) direction rotates, its top 20a2
(25a2) direction of rotation (arrow Da(Db) direction) front end portion crosses sliding contact terminal CEa(CEb), and 20 at the top of thisa2
(25a2), between inner peripheral surface 3a and side plate 35 generate gap, then as with as shown in dotted arrow, working oil becomes from the gap
Towards side plate 35 jet flow and be flowed into top 20a2(25a2) and top 20a3(25a3) between tooth socket.
Moreover, as shown in Figure 14 (c), if gear 20 (25) is further to arrow Da(Db) direction rotates, thus top
20a2(25a2), the gap between inner peripheral surface 3a and side plate 35 become larger, then top 20a2(25a2) and top 20a3(25a3) between
Working oil become high pressure PH。
In this way, if gear 20 (25) is continuously to arrow Da(Db) direction rotates, then may create the problem that from
Each top 20 of gear 20 (25)a(25a), be repeated in the gap to be formed between inner peripheral surface 3a and side plate 35 and generate towards side plate
35 jet flow generates gold because of the corrosion because the jet flow that the repetition generates causes to generate corrosion (erosion) on the surface of side plate 35
Belong to powder.
The present invention is completed in view of above actual conditions, it is designed to provide a kind of hydraulic pump, this is hydraulic
Pump uses helical gear, and can effectively inhibit and generate corrosion in side plate.
[technical means to solve problem]
It is related to a kind of hydraulic pump for solving the present invention of described problem, has:
A pair of of helical gear has the rotary shaft being arranged in a manner of extending outward respectively from both ends of the surface, and teeth portion phase
Mutually engagement；
Ontology, both ends opening, and there is the hydraulic pressure chamber for storing the pair of helical gear with meshing state in inside,
The hydraulic pressure chamber has the arc-shaped inner peripheral surface of the outer peripheral surface along each gear；
A pair of bearings component is disposed in the two sides of each gear in the hydraulic pressure chamber of the ontology, by each gear
Rotary shaft be freely and rotatably supported；
A pair of side plates is separately equipped in a manner of being connected to the end face of each helical gear in the pair of helical gear
Between the pair of parts of bearings；
Seal member is separately equipped between the pair of side plate and the pair of parts of bearings, will be formed in the side plate
Rear surface regions between parts of bearings are divided into 2 regions, and have elasticity；And
A pair of of lid is installed in the both ends of the surface of the ontology in the close shape of liquid respectively, the hydraulic pressure chamber is sealed；And
The pair of helical gear is with the specific sliding contact angular range in the engaging section than it by direction of rotation side
Interior, the mode with the inner peripheral surface sliding contact of the hydraulic pressure chamber is constituted respectively, and by the pair of side plate, the pair of spiral
The hydraulic area that the inner peripheral surface of the flank of tooth of gear and the hydraulic pressure chamber surrounds is set as follows: using the engaging section as boundary,
From the engaging section towards the direction of rotation, to the tooth of top universe and the forefront of the inner peripheral surface sliding contact of the hydraulic pressure chamber
Region until portion becomes low pressure, becomes high pressure than region of the teeth portion in front of direction of rotation,
It is made of as follows respectively each rear surface regions that the seal member is divided into 2 regions: wherein one
A region is connected to the hydraulic area of the high pressure, and is set as the more high pressure than another one region, as a region
High-pressure area range to reaching respectively with corresponding region in the sliding contact angular range, and the hydraulic pump is with as follows
Mode is constituted:
To in a pair of side plates for being connected to the helical gear along the tooth trace of the helical gear towards the side of each side plate
The side plate for becoming positive side to the direction of rotation relative to the helical gear, connects in the sliding of the pair of helical gear
In touching angular range in corresponding each region and position corresponding with the high-pressure area of the rear surface regions wear respectively from
Front penetrates into the through hole at the back side,
In the sliding contact angular range, by the teeth portion of the direction of rotation forefront of the helical gear, it is subsequent
Teeth portion, the pair of side plate and the hydraulic pressure chamber the high-pressure area of area of low pressure and the rear surface regions that surrounds of inner peripheral surface
It is connected to via the through hole.
As described above, a pair of of helical gear is in the hydraulic pump to lean on the specific of direction of rotation side in the engaging section than it
Sliding contact angular range in, the mode with the inner peripheral surface sliding contact of hydraulic pressure chamber is constituted respectively.Moreover, by a pair of side plates,
It is revolved using engaging section as boundary from the engaging section direction hydraulic area that the flank of tooth of a pair of of helical gear and the inner peripheral surface of hydraulic pressure chamber surround
Turning direction, the region until the teeth portion of the forefront of the inner peripheral surface sliding contact of top universe and hydraulic pressure chamber becomes low pressure, than
Region of the teeth portion in front of direction of rotation becomes high pressure.
In addition, being made of as follows respectively each rear surface regions that seal member is respectively divided into 2 regions: at least it
A region be connected to the hydraulic area of high pressure, and be set as with the high-pressure side of the hydraulic area be uniform pressure height
Pressure, the range of the high-pressure area as a region to reach respectively with corresponding area in the sliding contact angular range
Domain.
Moreover, constituting as follows: along the tooth trace court of helical gear in a pair of side plates for being connected to helical gear
The side plate for becoming positive side relative to the direction of rotation of helical gear to the direction of each side plate, with the pair of helical tooth
Position corresponding with the high-pressure area of the rear surface regions in corresponding each region in the sliding contact angular range of wheel, wears point
Do not penetrate into front and the back side through hole, in the sliding contact angular range, by helical gear direction of rotation most before
The area of low pressure and the rear surface regions that the teeth portion of side, the inner peripheral surface of its subsequent teeth portion, a pair of side plates and hydraulic pressure chamber surround
High-pressure area is connected to via the through hole.
In this way, in the hydraulic pump, along the helical gear of specific direction rotation teeth portion and be in sliding contact angular range
In interior teeth portion, that is to say, that in the teeth portion of the inner peripheral surface sliding contact of the top universe and hydraulic pressure chamber of teeth portion, direction of rotation is most
The teeth portion in front is before being more than sliding contact angular range and moving to its outside, the working fluid of the high pressure of rear surface regions
The inner peripheral surface of teeth portion by the forefront, its subsequent teeth portion, a pair of side plates and hydraulic pressure chamber is flowed into via the through hole
The area of low pressure (rear area) of encirclement, as a result, the rear area becomes high pressure.
In this way, before the teeth portion in the forefront is more than sliding contact angular range and moves to its outside, it is described
Rear area becomes high pressure, so that the region before and after the teeth portion becomes identical high pressure, so the teeth portion in forefront is more than to slide
When moving contact angle range and being left from the inner peripheral surface of hydraulic pressure chamber, even if in the teeth portion phase of the inner peripheral surface, side plate and helical gear
Gap is formed between mutually, working fluid will not be generated from the phenomenon that gap is flowed into towards rear area is formed by, therefore, no
It can generate to generate in side plate and corrode this conventional problems.
Although in addition, the working fluid of the high pressure of the rear surface regions is via the through hole and towards the rear area
It flows into, but since its inflow direction is approximately along the direction of the flank of tooth of teeth portion, so being difficult to generate corrosion in the teeth portion.
In addition, preferably described each through hole expands towards the helical gear lateral aperture in the hydraulic pump.Pass through
It is set as the shape of borehole enlargement like this, is able to suppress the flowing removing of working fluid.
[The effect of invention]
As described above, in hydraulic pump of the invention, in the teeth portion of helical gear in sliding contact angular range
Forefront teeth portion be more than sliding contact angular range and to its outside expose before, the working oil of the high pressure of rear surface regions
The rear area of the teeth portion is flowed into and the through hole of side plate is set, so that the rear area becomes high pressure, the teeth portion
The region of front and back become identical high pressure, so forefront teeth portion be more than sliding contact angular range and out of hydraulic pressure chamber
When circumferential surface leaves, even if the teeth portion in the inner peripheral surface, side plate and helical gear forms gap between each other, work will not be generated
Oil is from the phenomenon that gap is flowed into towards rear area is formed by, and therefore, will not generate and generate corrosion in side plate this is previous
Problem.
Detailed description of the invention
Fig. 1 is the positive view for indicating the oil pressure pump of one embodiment of the present invention.
Fig. 2 is the cross-sectional view in the arrow view direction A'-A' in Fig. 1.
Fig. 3 is the side view for indicating the side plate of present embodiment.
Fig. 4 is the explanatory diagram for indicating to be formed in the shape of through hole of side plate.
Fig. 5 is the explanatory diagram for the effect for illustrating the oil pressure pump of present embodiment.
Fig. 6 is the positive view for indicating previous oil pressure pump.
Fig. 7 is the cross-sectional view in the arrow view direction A-A in Fig. 6.
Fig. 8 is the side view for indicating the side plate of previous oil pressure pump shown in fig. 6.
Fig. 9 is the front view for indicating the bushing of previous oil pressure pump shown in fig. 6.
Figure 10 is the right side view of bushing shown in Fig. 9.
Figure 11 is to indicate to install in the bushing of Figure 10 to divide the right side view of the state of sealing element.
Figure 12 is the perspective view of the helical gear for indicating previous oil pressure pump shown in fig. 6, side plate and bushing.
Figure 13 is the cross-sectional view in the arrow view direction B-B in Fig. 6.
Figure 14 is the explanatory diagram for illustrating the problems in previous oil pressure pump point.
Specific embodiment
Hereinafter, description of specific embodiments of the present invention for the FIG. 1 to FIG. 5 based on attached drawing.Fig. 1 is to indicate the present invention
An embodiment oil pressure pump positive view, Fig. 2 be in Fig. 1 arrow view the direction A'-A' cross-sectional view.In addition, Fig. 3 is table
Show that the side view of the side plate of the oil pressure pump of this example, Fig. 4 are the explanatory diagrams for indicating to be formed in the shape of through hole of side plate, Fig. 5 is
For illustrate this example oil pressure pump effect explanatory diagram.
In addition, as shown in FIG. 1 to 3, the oil pressure pump 100 of this example other than the composition of side plate 135, have with Fig. 6~
The previous identical composition of oil pressure pump 1 shown in Figure 13.Therefore, in FIG. 1 to FIG. 5, to structure identical with previous oil pressure pump 1
At partially marking identical symbol, and explanation described above is applied for identical composition part, hereinafter, omitting the detailed of it
It describes in detail bright.In addition, also in the same manner as previous oil pressure pump 1, Self cleavage is carried out by elimination run in the oil pressure pump 100 of this example,
And become the state of the inner peripheral surface 3a sliding contact of gear 20,25 and hydraulic pressure chamber 4.
As described above, in the oil pressure pump 100, the composition and the composition of the side plate 35 of previous oil pressure pump 1 of the side plate 135
It is different.The side plate 135 is as shown in Figure 1, along the tooth trace of gear 20,25 towards the direction of the side plate 135 relative to gear 20,25
Direction of rotation become forward direction.On the other hand, side plate 30 along gear 20,25 tooth trace towards the direction of the side plate 30 relative to
The direction of rotation of gear 20,25 becomes reverse.
Side panel 135 is illustrated in Fig. 3, which has face shaping identical with side plate 35 shown in Fig. 8, with
The different aspect of side plate 35 be only that have penetrate into front and the back side through hole 135a,
135b.In addition, symbol 136,137 be with the through hole 36,37 corresponding through holes, symbol 138,139 be with
The lubrication groove 38,39 corresponding lubrication grooves.
The through hole 135a is located at the sliding contact angular range, theta of the gear 20a3It is interior, and be arranged and leading to by institute
State the position for dividing the high-pressure area 56a for the rear surface regions 56 that sealing element 55 divides.Through hole 135b similarly, is located at gear
25 sliding contact angular range, thetab3It is interior, and the height for leading to the rear surface regions 56 divided by the division sealing element 55 is set
The position of intermediate pressure section 56a.
As described above, dividing sealing element 55 is that the rear surface regions 56 that will be formed between bushing 45 and side plate 135 are divided into
The sealing element of high-pressure area 56a and area of low pressure 56b, and as shown in figure 3, high-pressure area 56a to the cunning reached with gear 20
Dynamic contact angle range Thetaa3Inside and gear 25 sliding contact angular range, thetab3The corresponding region in inside.
In addition, in Fig. 3, from vertical reference line r to angle, θa1Position be inner circumferential of the gear 20 relative to hydraulic pressure chamber 4
Face 3a starts the position of sliding contact, from reference line r to angle, θa2Position be terminate sliding contact position.Similarly, from
Reference line r is to angle, θb1Position be position that gear 25 starts sliding contact relative to the inner peripheral surface 3a of hydraulic pressure chamber 4, from benchmark
Line r is to angle, θb2Position be terminate sliding contact position.In addition, CEaIndicate that gear 20 terminates the position of sliding contact,
CEbIndicate that gear 25 terminates the position of sliding contact.
It in general can be that circular hole can also as its variation shown in these through holes 135a, 135b such as Fig. 4 (a)
For as shown in Fig. 4 (b) to shape (through hole 135a', 135b') made of gear 20,25 chamferings side-draw, alternatively, can also be
Make conical by its shape made of borehole enlargement (through hole 135a ", 135b ") in gear 20,25 sides as shown in Fig. 4 (c).
In the oil pressure pump 100 of this example for having the above composition, in the same manner as the oil pressure pump 1, firstly, work will be connected to
What the piping for making the hold-up tank of oil was connected to shell 2 is taken into hole 5, and the piping that will be connected to oil pressure unit is connected to squit hole 6, and
And be connected to drive motor after the rotary shaft 21 of the driving gear 20, make that gear 20 is driven to revolve using the drive motor
Turn.
The rotation of driven gear 25 engage as a result, with driving gear 20, by the inner peripheral surface 3a of hydraulic pressure chamber 4, gear 20,25
The working oil for the hydraulic area that teeth portion and side plate 30,135 clip is transferred by the rotation of gear 20,25 to 6 side of squit hole, with
The engaging section of gear 20,25 is boundary, sliding to the inner peripheral surface 3a of top universe and hydraulic pressure chamber 4 from the engaging section towards direction of rotation
Become low pressure comprising being taken into the region including hole 5 until the teeth portion of the forefront of dynamic contact, than the teeth portion before direction of rotation
Side becomes high pressure comprising the region including squit hole 6, and the working oil for being pressurized to high pressure is conveyed via squit hole 6 and piping
To oil pressure unit.
In addition, being divided sealing element 50,55 to be respectively divided into each rear surface regions 51,56 in 2 regions is respectively higher-pressure region
Domain 51a, 56a are connected to the hydraulic area of high pressure, become high pressure identical with the hydraulic area of the high pressure, another area of low pressure
51b, 56b are connected to the hydraulic area of low pressure, become low pressure identical with the hydraulic area of the low pressure.
Moreover, in the side plate 135 that described through hole 135a, 135b is arranged, working oil by through hole 135a,
135b shows behavior as shown in Figure 5.In addition, Fig. 5 is figure corresponding with described Figure 14, and it is comparable to the view of the arrow in Figure 12 C
The figure in direction.In addition, being shown in Fig. 5 to gear 20, but also identical about gear 25, so will be with the gear 25
Relevant symbol is marked with parantheses.In addition, symbol 20a1(25a1)、20a2(25a2)、20a3(25a3) and 20a4(25a4) it is respectively tooth
The top (crest line) in portion.
In Fig. 5, gear 20 (25) is to arrow Da(Db) direction rotates, in Fig. 5 (a), than the cunning indicated with two o'clock chain line
Dynamic contact terminal CEa(CEb) top 20 on the upstream sidea2(25a2)、20a3(25a3) and 20a4(25a4) universe and hydraulic pressure chamber 4
On the other hand inner peripheral surface 3a sliding contact is more than sliding contact terminal CEa(CEb) top 20a1(25a1) at least part
Not with inner peripheral surface 3a sliding contact.Moreover, as shown in the Fig. 5 (a), top 20a1(25a1) and top 20a2(25a2) between work
Making oil becomes high pressure PH, top 20a2(25a2) and top 20a3(25a3) between working oil become high pressure PH, top 20a3(25a3)
With top 20a4(25a4) between working oil become low pressure PL。
Secondly, as shown in Fig. 5 (b), gear 20 (25) is to arrow Da(Db) direction rotates, at top 20a3(25a3) it is more than to slide
Dynamic contact terminal CEa(CEb) before, the through hole 135a (135b) is 20 at the top of thisa3(25a3) and top 20a4(25a4) it
Between tooth socket opening, so that they become states of connection, at this point, as shown in the arrow with dotted line, the rear surface regions of high pressure
The working oil of 56a is flowed into than top 20a3(25a3) region rearward, that is, top 20a3(25a3) and top 20a4
(25a4) between tooth socket, as a result, the tooth socket (rear area) becomes high pressure P as shown in Fig. 5 (c)H.At this point, from high pressure
Rear surface regions 56a be flowed into the working oil of the tooth socket (rear area) since its inflow direction becomes approximately along the tooth
The direction of the flank of tooth in portion, so being difficult to generate corrosion in the teeth portion.
On the other hand, even if top 20a2(25a2) direction of rotation (arrow Da(Db) direction) front end portion crosses sliding and connect
Touch terminal CEa(CEb), and 20 at the top of thisa2(25a2), between inner peripheral surface 3a and side plate 35 generate gap, due to than the top
20a2(25a2) region (top 20 on the fronta1(25a1) and top 20a2(25a2) between tooth socket) and than the top 20a2
(25a2) region (top 20 rearwarda2(25a2) and top 20a3(25a3) between tooth socket) have become identical high pressure,
So the phenomenon that region of the working oil from the gap towards rear flows into will not be generated.
In this way, being in sliding contact angular range, theta in the oil pressure pump 100 of this examplea3(θb3) in direction of rotation most
The teeth portion in front is more than the sliding contact angular range, thetaa3(θb3) and be moved to before its outside, that is to say, that it is being more than institute
State sliding contact terminal CEa(CEb) before, the working oil of high pressure is flowed by the through hole 135a (135b) from rear surface regions 56a
Enter the region to its rear, so that the rear area becomes high pressure, so the teeth portion in forefront crosses sliding contact terminal CEa
(CEb) and when being left from the inner peripheral surface 3a of hydraulic pressure chamber 4, even if in the teeth portion phase of inner peripheral surface 3a, side plate 135 and gear 20 (25)
Gap is formed between mutually, the phenomenon that working oil is flowed into from the region for being formed by gap towards rear will not be generated, therefore, no
It can generate to generate in side plate and corrode this conventional problems.
In addition, in the oil pressure pump 100, such as Fig. 4 (b) and (c) shown in, preferably described each through hole 135a, 135b court
Expand to gear 20,25 lateral apertures.By being set as the shape of borehole enlargement like this, it is able to suppress the flowing removing of working oil.
More than, one embodiment of the present invention is illustrated, but the adoptable specific form of the present invention is not by this
Any restriction of embodiment.
For example, helical gear 20,25 is set as with the helical gear such as lower toothed (even in the oil pressure pump 100 of upper example
Line meshing gear is touched in continued access), that is, include respectively arc sections in tooth top and bottom of the tooth, is formed in engaging section from the one of tooth width direction
A end is to the continuous contact line in another end, and but not limited to this, also can be set to other tooth forms (comprising well known one
As tooth form) helical gear.
In addition, as long as the position of setting through hole 135a, 135b are the position for playing the effect, that is, in cunning
Dynamic contact angle range Thetaa3(θb3) in direction of rotation forefront teeth portion be more than the sliding contact angular range, thetaa3(θb3) to it
Outside it is mobile before, that is to say, that crossing the sliding contact terminal CEa(CEb) before, the working oil of high pressure is by being somebody's turn to do
Through hole 135a (135b) is flowed into the position in the region at its rear from rear surface regions 56a, then can be any position.
As long as its size is simultaneously unlimited in addition, the internal diameter of through hole 135a, 135b are the negotiable size of working oil
System.
In addition, the shape of through hole 135a, 135b are not limited to circular hole, it can also be the other shapes such as long hole or square hole.
In addition, in the oil pressure pump 100 of upper example, make to drive the direction of rotation of gear 20 from 7 side of front cover when dextrorotation
Turn, to driving gear 20 using the helical gear of right torsion, uses driven gear 25 helical gear of left handed twist, but and unlimited
Due to this, can also make the direction of rotation of sliding tooth wheel 20 from 7 side of front cover when anticlockwise, to driving gear use left torsion
The helical gear turned uses driven gear the helical gear of right torsion.
In turn, in upper example, hydraulic pump of the invention is set as oil pressure pump and is embodied, but not limited to this, for example,
Also it can be set to the cooling pump using cutting fluid as working fluid and embody.
[description of symbols]
1 oil pressure pump
2 shells
3 ontologies
3a inner peripheral surface
4 hydraulic pressure chambers
7 front covers
8 end caps
20,25 (spiral) gear
21,22,26,27 rotary shaft
30,35 side plate
40,45 bushing
40a, 45a seal groove
50,55 sealing element is divided
100 oil pressure pumps
135 side plates
135a, 135b through hole
θa3、θb3Sliding contact angular range
Claims (2)
1. a kind of hydraulic pump, has:
A pair of of helical gear has the rotary shaft being arranged in a manner of extending outward respectively from both ends of the surface, and teeth portion is mutually nibbled
It closes；
Ontology, both ends opening, and in the internal hydraulic pressure chamber for having and storing the pair of helical gear with meshing state, the liquid
Pressure chamber has the arc-shaped inner peripheral surface of the outer peripheral surface along each gear；
A pair of bearings component is disposed in the two sides of each gear in the hydraulic pressure chamber of the ontology, by the rotation of each gear
Shaft is freely and rotatably supported；
A pair of side plates is separately equipped in a manner of being connected to the end face of each helical gear in the pair of helical gear and institute
It states between a pair of bearings component；
Seal member is separately equipped between the pair of side plate and the pair of parts of bearings, will be formed in the side plate and axis
Rear surface regions between bearing portion part are divided into 2 regions, and have elasticity；And
A pair of of lid is installed in the both ends of the surface of the ontology in the close shape of liquid respectively, the hydraulic pressure chamber is sealed；And
The pair of helical gear is to divide in the specific sliding contact angular range that the engaging section than it leans on direction of rotation side
Mode not with the inner peripheral surface sliding contact of the hydraulic pressure chamber is constituted, and by the pair of side plate, the pair of helical gear
The flank of tooth and the hydraulic pressure chamber inner peripheral surface surround hydraulic area set as follows: using the engaging section as boundary, from this
Engaging section is towards the direction of rotation, to top universe and the teeth portion of the forefront of the inner peripheral surface sliding contact of the hydraulic pressure chamber
Region only becomes low pressure, becomes high pressure than region of the teeth portion in front of direction of rotation,
It is made of as follows respectively each rear surface regions that the seal member is divided into 2 regions: one of area
Domain is connected to the hydraulic area of the high pressure, and is set as the more high pressure than another one region, the height as a region
The range of intermediate pressure section to reach respectively with corresponding region in the sliding contact angular range；And the feature of the hydraulic pump exists
In composition as follows:
To in a pair of side plates for being connected to the helical gear along the tooth trace of the helical gear towards the direction phase of each side plate
The side plate for becoming positive side for the direction of rotation of the helical gear, at the sliding contact angle of the pair of helical gear
It is worn respectively in degree range in corresponding each region and in position corresponding with the high-pressure area of the rear surface regions from front
The through hole at the back side is penetrated into,
In the sliding contact angular range, by the teeth portion of the direction of rotation forefront of the helical gear, its subsequent tooth
The high-pressure area of area of low pressure and the rear surface regions that the inner peripheral surface in portion, the pair of side plate and the hydraulic pressure chamber surrounds via
The through hole and be connected to.
2. hydraulic pump according to claim 1, it is characterised in that: each through hole is towards the helical gear lateral aperture
Expand.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2016-053335 | 2016-03-17 | ||
| JP2016053335A JP6668121B2 (en) | 2016-03-17 | 2016-03-17 | Hydraulic equipment |
| PCT/JP2017/004688 WO2017159135A1 (en) | 2016-03-17 | 2017-02-09 | Hydraulic device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN108291539A CN108291539A (en) | 2018-07-17 |
| CN108291539B true CN108291539B (en) | 2019-08-09 |
Family
ID=59851179
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201780003969.6A Expired - Fee Related CN108291539B (en) | 2016-03-17 | 2017-02-09 | Hydraulic device |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JP6668121B2 (en) |
| CN (1) | CN108291539B (en) |
| WO (1) | WO2017159135A1 (en) |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH02291488A (en) * | 1989-04-30 | 1990-12-03 | Shimadzu Corp | Gear pump |
| JPH08121352A (en) * | 1994-10-31 | 1996-05-14 | Shimadzu Corp | Gear pump or motor |
| WO2001009514A1 (en) * | 1999-07-30 | 2001-02-08 | Hitachi, Ltd. | Gear pump and method of assembling the gear pump |
| CN203809288U (en) * | 2013-11-27 | 2014-09-03 | 住友精密工业股份有限公司 | Hydraulic device |
| CN104583598A (en) * | 2013-06-27 | 2015-04-29 | 住友精密工业股份有限公司 | Hydraulic device |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR100255726B1 (en) * | 1993-03-31 | 2000-05-01 | 윤종용 | Automatic frequency control method and apparatus |
-
2016
- 2016-03-17 JP JP2016053335A patent/JP6668121B2/en not_active Expired - Fee Related
-
2017
- 2017-02-09 WO PCT/JP2017/004688 patent/WO2017159135A1/en active Application Filing
- 2017-02-09 CN CN201780003969.6A patent/CN108291539B/en not_active Expired - Fee Related
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH02291488A (en) * | 1989-04-30 | 1990-12-03 | Shimadzu Corp | Gear pump |
| JPH08121352A (en) * | 1994-10-31 | 1996-05-14 | Shimadzu Corp | Gear pump or motor |
| WO2001009514A1 (en) * | 1999-07-30 | 2001-02-08 | Hitachi, Ltd. | Gear pump and method of assembling the gear pump |
| CN104583598A (en) * | 2013-06-27 | 2015-04-29 | 住友精密工业股份有限公司 | Hydraulic device |
| CN203809288U (en) * | 2013-11-27 | 2014-09-03 | 住友精密工业股份有限公司 | Hydraulic device |
Also Published As
| Publication number | Publication date |
|---|---|
| CN108291539A (en) | 2018-07-17 |
| JP6668121B2 (en) | 2020-03-18 |
| WO2017159135A1 (en) | 2017-09-21 |
| JP2017166432A (en) | 2017-09-21 |
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