WO2015045744A1 - オイルポンプ - Google Patents
オイルポンプ Download PDFInfo
- Publication number
- WO2015045744A1 WO2015045744A1 PCT/JP2014/072880 JP2014072880W WO2015045744A1 WO 2015045744 A1 WO2015045744 A1 WO 2015045744A1 JP 2014072880 W JP2014072880 W JP 2014072880W WO 2015045744 A1 WO2015045744 A1 WO 2015045744A1
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- WIPO (PCT)
- Prior art keywords
- rotor
- cam
- volume
- outer rotor
- amount
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
- F04C14/18—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber
- F04C14/22—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members
- F04C14/223—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members using a movable cam
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C13/00—Adaptations of machines or pumps for special use, e.g. for extremely high pressures
- F04C13/001—Pumps for particular liquids
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
- F04C15/06—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C2/32—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in groups F04C2/02 and relative reciprocation between co-operating members
- F04C2/332—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in groups F04C2/02 and relative reciprocation between co-operating members with vanes hinged to the outer member and reciprocating with respect to the inner member
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
- F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
- F04C2/3448—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member with axially movable vanes
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2210/00—Fluid
- F04C2210/20—Fluid liquid, i.e. incompressible
- F04C2210/206—Oil
Definitions
- the present invention relates to an oil pump, and more particularly, to an oil pump including an inner rotor, an outer rotor, and a plurality of vanes that connect an outer peripheral portion of the inner rotor and an inner peripheral portion of the outer rotor.
- an oil pump including an inner rotor, an outer rotor, and a plurality of vanes that connect the outer peripheral portion of the inner rotor and the inner peripheral portion of the outer rotor.
- Such an oil pump is disclosed in, for example, Japanese Patent Application Laid-Open No. 2012-255439.
- JP 2012-255439 A an inner rotor that is rotationally driven, an outer rotor that is disposed so as to surround the inner rotor and is configured to be rotatable outside the inner rotor, and an outer peripheral portion of the inner rotor and an inner peripheral portion of the outer rotor are connected to each other.
- a pendulum slider pump (oil pump) having a plurality of pendulums (vanes) is disclosed.
- one end portion (tip portion) of each pendulum is hingedly connected to the outer peripheral portion of the inner rotor, and the other end portion (root portion) is connected to each other.
- each pendulum is sequentially rotated while swinging around the connecting portion with the inner rotor as the inner rotor rotates, and the other end of the pendulum is recessed in the outer rotor. It can be displaced freely.
- the plurality of volume chambers individually partitioned by the pendulum are configured to generate a pump function by sequentially repeating deformation with the rotation of the inner rotor.
- each pendulum has an intermediate portion connecting one end and the other end narrower than both ends (one end and the other end). Yes. This prevents the intermediate portion entering the recess of the outer rotor from coming into contact with the inner wall of the recess due to the swing (inclination) of the pendulum.
- the individual pendulums swing in a pendulum shape so that the inner rotor and the outer rotor having relative eccentricity rotate smoothly together.
- the present invention has been made to solve the above problems, and one object of the present invention is to provide an oil pump capable of sufficiently increasing the net discharge amount of oil per unit rotation. It is to be.
- an oil pump includes a vane housing portion in which a plurality of vanes are housed so as to be slidable in a radial direction, a rotatable inner rotor, and a plurality of vanes.
- the second volume changes by changing the circumferential distance between the adjacent vane connecting portions provided in the outer rotor and the first rotor that has a pump function according to the eccentricity of the inner rotor with respect to the outer rotor.
- a second volume changing unit having a pump function.
- the inner rotor including the vane accommodating portion in which the plurality of vanes are accommodated so as to be slidable in the radial direction is connected to the radially outer tips of the plurality of vanes.
- a second volume changing portion having a pump function is provided by changing the second volume by changing the circumferential distance between adjacent vane connecting portions.
- the pump operation of the 2nd volume change part newly provided in the outer rotor can also be utilized effectively. Therefore, the net discharge amount of oil per unit rotation in the oil pump can be sufficiently increased. As a result, pump efficiency can be improved.
- the oil pump can be reduced in size, so that the mountability of the oil pump to a device (apparatus) can be improved. Further, since the oil pump is reduced in size, mechanical loss (mechanical loss) when the oil pump is driven can be reduced, so that the load of the drive source that drives the oil pump is reduced, and energy saving can be achieved. .
- the pump function is preferably performed by changing the third volume in the vane housing portion of the inner rotor by sliding the plurality of vanes in the radial direction according to the eccentricity of the inner rotor with respect to the outer rotor.
- a third volume changing unit If comprised in this way, in addition to the pump operation
- the pendulum that swings in a pendulum shape has an intermediate portion that is narrower than both ends, and therefore, the other end portion (root portion) of the pendulum enters deeply into the recess of the outer rotor and In the process of minimizing the volume chamber surrounded by the concave portion, a new space portion (volume portion) is generated secondarily between the narrowed middle portion of the pendulum and the concave portion.
- the vane that is linearly slid and moved in the radial direction since the vane that is linearly slid and moved in the radial direction is used, it is not necessary to narrow the intermediate portion of the vane that appears and disappears with respect to the vane housing portion. Therefore, in the process in which the third volume changing unit causes the volume change in the direction of decreasing the third volume, the volume is newly increased at the first volume changing unit side of the third volume changing unit (the volume chamber is newly set). Since no negative factor (unnecessary work) occurs, the volume changes of the first, second, and third volume changing sections can be effectively applied to the pump operation of the entire oil pump.
- the apparatus further includes a suction port for sucking oil and a discharge port for discharging oil, and the vane accommodated in the vane accommodating section is gradually increased radially outward.
- the third volume in the vane accommodating portion of the inner rotor gradually increases, and at the discharge port, the vane accommodated in the vane accommodating portion gradually slides radially inward, so that the vane of the inner rotor It is comprised so that the 3rd volume in an accommodating part may become small gradually.
- the volume change of the 3rd volume which repeats appearing (increase) and disappearance (decrease) in a vane accommodating part with the linear reciprocation of the vane to the radial direction outer side and inner side direction as pump operation
- the volume change of the first volume change portion (first volume) and the second volume change portion (second volume) accompanying the sliding movement of the vane but also the first driving force of the oil pump accompanying the slide movement of the vane. Since it can also be converted into a volume change of the three volume changing portion (third volume), the driving force is not wasted and the mechanical efficiency of the oil pump can be improved.
- the thickness of the vane in the portion accommodated in the vane accommodating portion is preferably constant. If comprised in this way, the vane by which the thickness of the part accommodated in a vane accommodating part became fixed can be slid and moved stably to a radial direction, without shaking a vane in a vane accommodating part. Further, since the vane does not rattle during the reciprocating movement, it is possible to improve the airtightness when the third volume change portion (third volume) repeats expansion (increase) and reduction (decrease). Thereby, the pump efficiency of a 3rd volume change part can be maintained at a high level.
- the second volume changing portion includes a plurality of outer rotor rotors configured by changing a radial slide position of a radially outer tip of the vane in accordance with an eccentricity of the inner rotor with respect to the outer rotor.
- the circumferential distance between the vane connecting portions is configured so that the second volume can be changed
- the outer rotor is provided for each of the plurality of vanes, and includes a plurality of outer rotor pieces each including the vane connecting portion, The plurality of outer rotor pieces are arranged circumferentially in a state where adjacent outer rotor pieces are engaged with each other so that the distance in the circumferential direction can be changed.
- the adjacent outer rotor pieces constitute a second volume changing portion.
- the circumferential distance between the adjacent outer rotor pieces is changed while engaging with each other in the circumferential direction. It is configured such that the second volume of the engagement space is changed. If comprised in this way, the distance of the circumferential direction between the several vane connection parts in an outer rotor will be easily changed (expanded) suitably using the displacement of the radial slide position of the front-end
- a plurality of outer rotor pieces are arranged in a circumferential shape with adjacent outer rotor pieces engaged with each other in such a manner that their circumferential distances can be changed.
- the second volume changing portion second volume
- the engagement space when the outer rotor pieces are engaged with each other is appropriately used as the second volume.
- the second volume changing unit can exhibit a pump function in which the second volume repeatedly increases and decreases.
- the engagement space constituting the second volume changing portion and the first volume changing portion are communicated. Grooves or holes are provided.
- the first volume changing portion having the first volume and the second volume changing portion having the second volume are communicated with each other through the groove or the hole, so that the oil is supplied when the volume chamber is expanded. Both the first volume change unit and the second volume change unit can inhale. Further, when the volume chamber is reduced, oil can be discharged from both the first volume change portion and the second volume change portion.
- the engagement space forming the second volume change portion is preferably adjacent.
- a first engagement space located on one side of the two vanes and a second engagement space located on the other side of the two adjacent vanes are included.
- the second volume changing portion can change the second volume according to the eccentricity of the inner rotor with respect to the outer rotor
- the second volume changing portion further includes a suction port for sucking oil and a discharge port for discharging oil
- the outer rotor has a plurality of A plurality of outer rotor pieces that are provided for each vane and each include a vane connecting portion, and in the suction port, the circumferential distance between adjacent outer rotor pieces gradually increases, and the second volume gradually increases.
- the discharge port is configured such that the second volume gradually decreases as the circumferential distance between adjacent outer rotor pieces gradually decreases.
- the rotor accommodating portion that accommodates the inner rotor and is movable in the first direction so as to change the eccentric amount of the inner rotor, the suction port for sucking oil, and the discharge port for discharging oil And linearly moved in a second direction intersecting the first direction in accordance with the oil discharge pressure from the discharge port, and the rotor accommodating portion is moved to the first direction along the linear movement in one direction of the second direction.
- a cam member including a cam region provided to increase or decrease the amount of eccentricity of the inner rotor by moving in the direction.
- a rotor accommodating part will be 1st direction via the cam area
- the amount of eccentricity of the inner rotor can be easily changed by increasing or decreasing it. Therefore, in the present invention, the amount of eccentricity of the inner rotor can be increased or decreased only by movement in one direction, so there is no need to switch the position of application of oil pressure according to the oil discharge pressure (rotation speed of the internal combustion engine). As a result, it is not necessary to provide a hydraulic direction switching valve or the like, and accordingly, the configuration of the oil pump can be further simplified.
- the cam member includes a spool member that is linearly moved in the second direction in accordance with an oil discharge pressure, and the rotor accommodating portion is formed of the spool member.
- a cam engaging portion disposed so as to face the cam region, and the cam region of the spool member has a protrusion amount with respect to the cam engaging portion of the rotor accommodating portion changed along the second direction, and the spool member The rotor accommodating portion is moved in the first direction in accordance with a change in the amount of protrusion of the cam region that accompanies movement in one direction of the second direction, so that the eccentric amount of the inner rotor is increased or decreased.
- the cam accompanying the movement to the one direction of the 2nd direction of a spool member will be utilized effectively using the cam mechanism comprised by the cam area
- the amount of eccentricity of the inner rotor can be increased or decreased by directly following the change in the protruding amount of the region.
- the cam region of the spool member preferably has the oil discharge pressure from the discharge port as the first pressure.
- the pressure is within the range, when the first cam region disposed opposite to the cam engagement portion of the rotor housing portion and the second pressure range where the oil discharge pressure from the discharge port is greater than the first pressure range, The cam engagement of the rotor accommodating portion when the second cam region engaged with the cam engaging portion of the rotor accommodating portion and the third pressure range where the oil discharge pressure from the discharge port is larger than the second pressure range.
- a cam region of the cam member to the first cam region, the second cam region, and the third cam region in response to an increase in oil discharge pressure from the discharge port.
- the amount of movement of the rotor accommodating portion in the first direction relative to the rotation center of the inner rotor and the amount of eccentricity of the inner rotor are reduced in the second cam region, and the second cam From the state in which the amount of movement of the rotor housing portion in the first direction relative to the rotation center of the inner rotor and the amount of eccentricity of the inner rotor are reduced in the region, the amount of movement of the rotor housing portion in the first direction and the amount of eccentricity of the inner rotor are reduced in the third cam region. It is configured to be increased.
- the oil discharge pressure is changed from the first pressure range to the second pressure range with reference to the first cam region corresponding to the case where the oil discharge pressure from the discharge port is in the first pressure range.
- the cam region of the spool member extends from the first cam region to the second cam region and from the second cam region along one direction of the second direction.
- the first cam region has an eccentric amount of the inner rotor accompanying the movement of the rotor accommodating portion in the first direction.
- the second cam region is formed so that the eccentric amount of the inner rotor accompanying the movement of the rotor accommodating portion in the first direction is a second eccentric amount smaller than the first eccentric amount.
- the third cam region is formed such that the amount of eccentricity of the inner rotor accompanying the movement of the rotor accommodating portion in the first direction becomes a third amount of eccentricity that is larger than the minimum value of the second amount of eccentricity.
- the pump capacity is smaller than the first pressure range when the oil discharge pressure is in the second pressure range.
- the pump displacement can be adjusted to be larger than the second pressure range and smaller than the first pressure range when the oil discharge pressure is in the third pressure range.
- the second cam region is provided such that the eccentric amount of the inner rotor decreases from the first eccentric amount to the second eccentric amount toward the third cam region.
- the eccentric amount of the inner rotor is provided so as to increase from the second eccentric amount to the third eccentric amount toward the side opposite to the two-cam region. If comprised in this way, in the 2nd cam area
- the first cam region of the spool member corresponds to the cam engaging portion of the rotor accommodating portion.
- the rotor accommodating portion is linearly moved to the first eccentric position in the first direction by being linearly moved to the position where the first eccentric amount is the first eccentric amount.
- the second cam region of the spool member is linearly moved to a position where the second cam region engages with the cam engaging portion of the rotor accommodating portion, so that the rotor accommodating portion is linearly aligned with the second eccentric position in the first direction.
- the second eccentric amount is smaller than the first eccentric amount
- the third cam region of the spool member engages with the cam engaging portion of the rotor accommodating portion in the third pressure range.
- rotor receiving portion is moved linearly in the third eccentric position in the first direction, and is configured to be larger third eccentricity than the minimum value of the second eccentricity. If comprised in this way, a rotor accommodating part will be moved to either the 1st eccentric position, the 2nd eccentric position, and the 3rd eccentric position which correspond in each of a 1st pressure range, a 2nd pressure range, and a 3rd pressure range.
- the eccentric amount of the inner rotor can be appropriately adjusted to the first eccentric amount, the second eccentric amount, and the third eccentric amount. Thereby, the oil pump which can exhibit the required discharge pressure characteristic exactly can be obtained.
- a first urging member that urges the rotor accommodating portion toward the cam member preferably, a first urging member that urges the rotor accommodating portion toward the cam member, and a first urging member that urges the cam member toward the position on the discharge port side.
- 2 further includes a biasing member. If comprised in this way, when a rotor accommodating part is moved to a 1st direction with the linear movement to the one direction of the 2nd direction of a cam member, the cam of a rotor accommodating part by a 1st biasing member The rotor accommodating portion can be moved in the first direction while appropriately following the cam shape (uneven shape) of the cam region of the cam member by the biasing force toward the member side.
- the urging force by the second urging member causes Since the cam member can be easily pushed back in the other direction opposite to the one direction of the second direction, a reversible operation according to the oil discharge pressure of the cam member can be performed.
- an oil film is preferably formed on the outer surface of the outer rotor. If comprised in this way, an outer rotor is included so that the shape change which changes the 2nd volume of a 2nd volume change part by changing the distance of the circumferential direction between the adjacent vane connection parts may be included including a plurality of vane connection parts. Even in the case of the configuration, since the oil film is formed on the outer surface of the outer rotor, the annular outer rotor with such a shape change can be smoothly rotated in the casing of the oil pump. Further, the second volume of the second volume changing portion can be smoothly changed by the oil film.
- the plurality of vanes are attached to the vane accommodating portion of the inner rotor so as to be slidable in the radial direction without swinging in the circumferential direction. If comprised in this way, since a vane can be made to appear and disappear with respect to a vane accommodating part with a linear (one-dimensional) slide movement along a radial direction at the time of oil-pump operation
- movement for example with respect to a vane accommodating part
- the outer rotor piece has an engagement piece portion that can be engaged in the circumferential direction in a state where the adjacent outer rotor pieces overlap each other in the radial direction, and the second volume
- the engagement space that constitutes the changing portion is configured such that the second volume is changed by changing the distance in the circumferential direction according to the amount of overlap between the engaging piece portions. If comprised in this way, since the 2nd volume of engagement space can be easily increased / decreased according to the overlap amount between the engagement piece parts which mutually overlap, a pump function is easily made to an outer rotor (2nd volume change part). Can be demonstrated.
- the cam region includes a first cam region, a second cam region, and a third cam region
- the first cam region, the second cam region, and the third cam region are continuous.
- the cam engaging portion of the rotor accommodating portion is moved in the first direction by sliding along at least the second cam region and the third cam region with the movement of the spool member. It is configured. With this configuration, when the spool member is moved in one direction of the second direction, the cam engagement portion is engaged so as to follow the cam shape of the cam region (second cam region and third cam region). Since the rotor accommodating portion can be moved in the first direction while being combined, the second cam region is based on the first cam region corresponding to the case where the oil discharge pressure from the discharge port is in the first pressure range. The eccentric amount of the inner rotor can be reduced smoothly, and the eccentric amount of the inner rotor can be increased smoothly from the reduced state in the third cam region.
- the cam member moves in the first direction of the rotor accommodating portion according to the change in the protruding amount of the cam region when the cam member is linearly moved in one direction of the second direction.
- the characteristic of the amount of eccentricity of the inner rotor due to movement in one direction has a hysteresis difference.
- the oil pump further including the rotor accommodating portion and the cam member
- at least a part of the oil sucked into the suction port is supplied to the cam region of the cam member.
- an oil pump capable of sufficiently increasing the net discharge amount of oil per unit rotation can be provided.
- FIG. 1 It is the perspective view which showed the structure of the spool member which comprises the oil pump by 3rd Embodiment of this invention. It is a figure for demonstrating operation
- FIG. 6 is a diagram showing characteristics of an oil pump (engine speed-discharge pressure characteristics) according to a third embodiment of the present invention and characteristics (engine speed-discharge pressure characteristics) of an oil pump as a comparative example with respect to the third embodiment. . It is a figure for demonstrating that the characteristic of the oil pump by 3rd Embodiment of this invention has a hysteresis difference. It is sectional drawing which showed the whole structure of the oil pump by 4th Embodiment of this invention.
- FIG. 10 is a diagram showing characteristics of an oil pump (engine speed-discharge pressure characteristics) according to a fourth embodiment of the present invention and characteristics (engine speed-discharge pressure characteristics) of an oil pump as a comparative example with respect to the third embodiment. . It is the top view which showed the structure of the outer rotor piece (single item) which comprises the pump element in the oil pump by the modification of this invention.
- the oil pump 100 includes an inner rotor 10, an outer rotor 20, and six vanes 30 that connect the inner rotor 10 and the outer rotor 20.
- the inner rotor 10, the outer rotor 20, and the six vanes 30 constitute a pump element 35 having a pump function.
- the oil pump 100 includes a housing 40 made of an iron-based metal material that accommodates the annular outer rotor 20 so as to be rotatable in the arrow Q2 direction, and the housing 40 is accommodated in a movable (Y direction).
- FIG. 1 in order to show the internal structure of the oil pump 100, the illustration of the housing 40 that houses the outer rotor 20 and the pump body 50 (see FIG. 2) is omitted.
- the oil pump 100 is configured to be mounted on, for example, an internal combustion engine (engine) (not shown). In this case, oil (lubricating oil) 1 (see FIG. 2) in the oil pan is moved around the piston or It has a function of supplying to a movable part (sliding part) such as a crankshaft.
- the oil pump 100 includes a suction port 52 that sucks in the oil 1 and a discharge port 53 that discharges the oil 1.
- the suction port 52 and the discharge port 53 are formed in the pump body 50 behind the housing 40 (back side in the drawing).
- the oil pump 100 also includes a cover (not shown) that covers the pump body 50 from the front side of the sheet.
- six volume chambers 61 each surrounded by the inner rotor 10, the outer rotor 20, and the six vanes 30 are formed in the pump body 50 closed by the cover.
- each volume chamber 61 has a volume V1.
- the volume V1 is configured to be increased or decreased according to a change (enlargement or reduction) of the volume chamber 61 accompanying expansion or contraction (sliding movement) of the vane 30 when the oil pump 100 is operated.
- the volume chamber 61 is an example of the “first volume changing portion” in the present invention.
- the volume V1 is an example of the “first volume” in the present invention.
- the inner rotor 10 made of an iron-based metal material has a shaft hole 11 in the center portion serving as the rotation center R. Further, when a drive shaft (not shown) is connected to the shaft hole 11, the inner rotor 10 is rotated in one direction (the direction of the arrow Q2) with the position of the rotation center R being fixed.
- the crankshaft of the internal combustion engine (engine) is used as a drive source for the inner rotor 10. Further, the inner rotor 10 has a vane accommodating portion 12 provided along the outer peripheral portion of the inner rotor 10.
- the vane accommodating portion 12 has six concave portions 12a extending in the radial direction from the outer peripheral portion of the inner rotor 10 toward the shaft hole 11 (rotation center R).
- the “radial direction” described here indicates a direction along the rotation radius when the inner rotor 10 is rotated around the rotation center R.
- Each of the recesses 12a has a predetermined depth in the radial direction, and the recesses 12a are arranged at equal angular intervals (60-degree intervals) with respect to the shaft hole 11.
- the recessed part 12a is extended in the groove shape along the X direction from the end surface of one side (X2 side) of the inner rotor 10 to the end surface of the other side (X1 side).
- the width W (see FIG.
- the inner rotor 10 has a predetermined rotor width L (see FIG. 1) along the X direction.
- the rotor width L is the same as the length (width) of the outer rotor 20 and the housing 40 in the X direction.
- the outer rotor 20 made of aluminum alloy has six outer rotor pieces 21 as shown in FIG. Further, the individual outer rotor pieces 21 are configured to be sequentially connected (engaged) in a circumferential shape. Thus, the outer rotor 20 is configured to rotate in the direction of the arrow Q2 with respect to the housing 40 in a state where the outer rotor piece 21 is connected in an annular shape along the inner peripheral surface 40a of the housing 40.
- the outer rotor piece 21 includes a first engagement piece portion 21a, a second engagement piece portion 21b, a third engagement piece portion 21c, and a fourth engagement portion each formed in a partial arc shape. And a piece 21d.
- the outer rotor piece 21 further includes a base portion 21e extending in the axial direction (X direction), and extends in the axial direction (X direction) on the Q2 side of the first engagement piece portion 21a and the fourth engagement piece portion 21d.
- the root portion is connected to the base portion 21e from the Q1 side.
- a root portion extending in the axial direction (X direction) on the Q1 side of the second engagement piece portion 21b and the third engagement piece portion 21c is connected to the base portion 21e from the Q2 side.
- the Q1 side and the Q2 side correspond to one side and the other side in the circumferential direction of the outer rotor piece 21, respectively.
- the outer rotor piece 21 has a shape in which the first engagement piece portion 21a to the fourth engagement piece portion 21d have arc-shaped blades spread in the circumferential direction (arrow Q1 direction and arrow Q2 direction) with the base portion 21e as the center. It is a monolithic component.
- the base 21e is an example of the “vane connecting portion” in the present invention.
- the first members are arranged diagonally with respect to the base 21e.
- the combined piece portion 21a and the third engagement piece portion 21c are disposed on the outer side in the radial direction of the outer rotor piece 21 (the front side in the drawing).
- the second engagement piece portion 21b and the fourth engagement piece portion 21d arranged in a diagonal relationship with each other are relative to the first engagement piece portion 21a and the third engagement piece portion 21c.
- the first engagement piece portion 21a to the fourth engagement piece portion 21d are in this order so as to have a staggered relationship (step difference) along the radial direction, such as radially outside, inside, outside, and inside. Is arranged. Further, as shown in FIG. 2, the outer surface 3 of each of the first engagement piece portion 21 a and the third engagement piece portion 21 c is circumferentially arranged with respect to the inner peripheral surface 40 a of the housing 40 via the oil film 1 a ( It is configured to slide in the direction of arrow Q).
- the first engagement piece portion of the outer rotor piece 21 on the Q2 side is connected.
- 21a is engaged with the second engagement piece portion 21b of the outer rotor piece 21 on the Q1 side so as to cover the outer side in the radial direction (front side in the drawing).
- the fourth engagement piece portion 21d of the outer rotor piece 21 on the Q2 side engages with the third engagement piece portion 21c of the outer rotor piece 21 on the Q1 side so as to enter the inner side in the radial direction (the back side in the drawing). Is done.
- the inner surface 2 on the radially inner side of the first engagement piece portion 21a on the Q2 side and the outer surface 3 on the radially outer side of the second engagement piece portion 21b relatively adjacent to the Q1 direction are provided. Abut (surface contact). Further, the outer surface 3 on the radially outer side of the fourth engagement piece portion 21d on the Q2 side relatively and the inner surface 2 on the radially inner side of the third engagement piece portion 21c relatively adjacent in the Q1 direction are provided. Abut (surface contact).
- the second engagement piece 21b and the third engagement piece 21c in 21 are alternately combined along the rotor width direction (X direction).
- the inner surface 2 and the outer surface of each of the first engaging piece portion 21a and the fourth engaging piece portion 21d on the Q2 side and the second engaging piece portion 21b and the third engaging piece portion 21c on the Q1 side. 3 is sequentially repeated on the outer rotor piece 21 adjacent along the Q direction.
- the six outer rotor pieces 21 are connected in an annular shape (circumferential shape) to constitute the outer rotor 20 (see FIG. 2).
- first engagement piece portion 21a to the fourth engagement piece portion 21d are formed in a partial arc shape, an overlap (an engagement area) in the circumferential direction (arrow Q direction) between the adjacent outer rotor pieces 21 is formed.
- ) Is configured to be increased or decreased along the arrow Q1 direction or the arrow Q2 direction within a predetermined range (range of the length of each piece in the circumferential direction).
- the outer rotor pieces 21 adjacent to each other are viewed from the side where the inner rotor 10 (see FIG. 2) is disposed. Therefore, the outer rotor 20 incorporated in the housing 40 (see FIG. 2) increases or decreases the distance (engagement area) in the circumferential direction (arrow Q direction) within a predetermined range between the adjacent outer rotor pieces 21. The engagement state between the two is maintained.
- the engagement spaces 5 to 8 described below are formed between the outer rotor pieces 21 adjacent to each other in the arrow Q direction.
- the first engagement piece portion 21a on the Q2 side of one outer rotor piece 21 and the second engagement piece portion of the outer rotor piece 21 adjacent to the Q1 side are firstly shown.
- one engagement space 5 is formed on the outer surface 3 side of the second engagement piece 21b so that the volume can be increased / decreased (expanded / contracted).
- the engagement space 5 is a space formed between the outer surface 3 of the second engagement piece 21b and the inner peripheral surface 40a (see FIG. 2) of the housing 40 facing the outer surface 3.
- the engagement space 5 is located on the Q1 side (one side) of the two adjacent vanes 30.
- one engagement space 6 is formed on the inner surface 2 side of the first engagement piece 21a so that the volume can be increased / decreased (expanded / contracted).
- the engagement space 6 is a space that is directly exposed to the inner rotor 10 (see FIG. 2) side.
- the engagement space 6 is located on the Q2 side (the other side) of the two adjacent vanes 30.
- the engagement spaces 5 and 6 are examples of the “first engagement space” and the “second engagement space” in the present invention, respectively.
- one notch 21f is formed at the connection between the base 21e and the second engagement piece 21b.
- the notch 21f has a predetermined length (depth) in the axial direction (X direction) from one end (X2 side) of the base 21e, and a part of the second engagement piece 21b is in the thickness direction. It is notched in a groove shape along. Thereby, the inner surface 2 side and the outer surface 3 side of the second engagement piece portion 21b communicate with each other.
- the chamber 61 is configured to communicate with each other through the notch 21f.
- the volume of the notch 21f is as small as possible with respect to the engagement space 5 in a range where the flow of the oil 1 is easily performed.
- the notch 21f is an example of the “groove” in the present invention.
- the outer rotor 20 has another similar configuration. As shown in FIGS. 5 and 6, the engagement between the fourth engagement piece portion 21d on the Q2 side of one outer rotor piece 21 and the third engagement piece portion 21c of the outer rotor piece 21 adjacent in the Q1 direction, One engagement space 7 capable of increasing / decreasing (extending / contracting) the volume is formed on the outer surface 3 side of the fourth engagement piece portion 21d.
- the engagement space 7 is a space formed between the outer surface 3 of the fourth engagement piece 21d and the inner peripheral surface 40a (see FIG. 2) of the housing 40 facing the outer surface 3. Further, as shown in FIG. 7, the engagement space 7 is located on the Q2 side (the other side) of two adjacent vanes 30.
- one engagement space 8 is formed on the inner surface 2 side of the third engagement piece 21c so that the volume can be increased or decreased (expanded / contracted).
- the engagement space 8 is a space that is directly exposed to the inner rotor 10 side.
- the engagement space 8 is located on the Q1 side (one side) of the two adjacent vanes 30.
- the engagement spaces 7 and 8 are examples of the “second engagement space” and the “first engagement space” in the present invention, respectively.
- the end portion where the first engagement piece portion 21a and the fourth engagement piece portion 21d face each other in the axial direction (X direction) extends from the end portion on the Q1 side along the circumferential direction (arrow Q direction) to the base portion.
- One notch 21g extending to 21e is formed.
- the notch portion 21g has a notch partly cut in a groove shape along the thickness direction in a state having a predetermined width in the X direction.
- the chamber 61 (refer FIG. 7) is comprised so that it may connect via the notch part 21g.
- the volume of the notch 21g is as small as possible with respect to the engagement space 7 in a range where the flow of the oil 1 is easily performed.
- the notch 21g is an example of the “groove” in the present invention.
- the engagement spaces 6 and 8 are disposed on the inner surface 2 side in the rotational radius direction of the outer rotor 20, the engagement spaces 6 and 8 are substantially the volume chamber 61. (See FIG. 7).
- the above-described engagement spaces 5, 6, 7 and 8 are configured so that one volume chamber 62 having a volume V2 is formed between the outer rotor pieces 21 engaged with each other. That is, the total volume of the engagement spaces 5 to 8 corresponds to the volume V2.
- the engagement spaces 6 and 8 are substantially in communication with the volume chamber 61, but here, the engagement spaces 6 and 8 are distinguished from the volume chamber 61 as an engagement space that can be increased or decreased formed on the outer rotor 20 side. Yes.
- the volume chamber 62 is configured so that each volume of the engagement spaces 5 to 8 is increased or decreased as the overlap (engagement area) in the circumferential direction (arrow Q direction) between the adjacent outer rotor pieces 21 is increased or decreased within a predetermined range.
- the increase / decrease operations are synchronized. That is, when the adjacent outer rotor pieces 21 are displaced in directions away from each other, the “overlap” is reduced, and the volume V2 with the engagement spaces 5 to 8 is monotonously increased. Further, when the adjacent outer rotor pieces 21 are displaced in a direction approaching each other, the “overlap” increases, and the volume V2 with the engagement spaces 5 to 8 is monotonously reduced. Further, the increase / decrease operation of each volume of the engagement spaces 5 to 8 plays a pump function of the outer rotor 20 described later.
- the volume chamber 62 is an example of the “second volume changing portion” in the present invention.
- the volume V2 is an example of the “second volume” in the present invention.
- the base portion 21e of the outer rotor piece 21 is formed with an engaging portion 21h having a predetermined inner diameter and a part of the inner side in the radial direction notched in a partial arc shape (C shape).
- the engaging portion 21h extends linearly from the end on one side (X2 side) along the axial direction of the base portion 21e to the end on the other side (X1 side), The engaging portion 21h penetrates the base portion 21e in the axial direction (X direction). That is, the length of the engaging portion 21h in the X direction is equal to the width of the vane 30 (the rotor width L of the inner rotor 10).
- the engaging portion 21h is an example of the “vane connecting portion” in the present invention.
- the side end portion 21j on the opposite side (Q1 side) from the base portion 21e of the first engagement piece portion 21a has a shape that is slightly tapered by reducing the thickness in the radial direction.
- the side end 21k opposite to the base 21e (Q2 side) of the three engagement piece 21c and the side end 21m on the Q2 side of the base 21e have a shape that is slightly tapered by reducing the thickness in the radial direction.
- Oil 1 (see FIG. 2) is easily drawn into Therefore, in the first embodiment, as shown in FIGS. 2 and 7, the outer rotor 20 is configured to rotate within the housing 40 in a state where the thin oil film 1 a is formed on the outer surface 20 a of the outer rotor 20. .
- the aluminum alloy vane 30 has a base portion 31 and a tip portion 32.
- the base portion 31 has a narrowed portion with a reduced thickness T on the distal end portion 32 side, and the distal end portion 32 is integrally connected to the tip of the narrowed portion.
- the base 31 has a root portion 31a.
- the vane 30 is configured to be inserted into the recess 12a (the vane housing portion 12) of the inner rotor 10 from the root portion 31a side.
- the base portion 31 is an example of the “portion accommodated in the vane accommodating portion” in the present invention.
- the thickness T of the base 31 is constant along the radial direction (moving direction of the vane 30).
- the width W of the concave portion 12a is formed to be a minute amount larger than the thickness T of the base portion 31, and the outer surface extending in the X direction of the base portion 31 has a rotation radius with respect to the inner surface extending in the X direction of the concave portion 12a. It is configured to slide smoothly (slide movement) along the direction. That is, the plurality of vanes 30 do not swing in the circumferential direction (arrow Q direction) that is the rotational direction of the inner rotor 10, and the tip 32 protrudes radially outward from the recess 12a, and vice versa.
- the base portion 31a is arranged in the concave portion 12a of the vane accommodating portion 12 of the inner rotor 10 so as to be able to perform a sliding movement operation that involves an operation of being pulled inward in the radial direction toward the concave portion 12a.
- a single volume chamber 63 having a volume V3 is formed in the vane accommodating portion 12 of the inner rotor 10 by the recess 12a and the root portion 31a of the vane 30. Further, the volume V3 of the volume chamber 63 is increased or decreased as the vane 30 is slidably moved relative to the recess 12a. That is, the volume V3 is increased when the vane 30 (tip portion 32) jumps out of the recess 12a, and the volume V3 is decreased when the vane 30 (root portion 31a) is drawn into the recess 12a.
- the volume chamber 63 is an example of the “third volume changing portion” in the present invention.
- the volume V3 is an example of the “third volume” in the present invention.
- the tip end portion 32 of the vane 30 is rounded, and the tip end portion 32 is configured to be fitted into an engaging portion 21 h formed on the base portion 21 e of the outer rotor piece 21.
- the cross-sectional area of the engaging portion 21h is formed to be a minute amount larger than the cross-sectional area of the tip portion 32, and the outer peripheral surface of the tip portion 32 has a slight gap with respect to the inner peripheral surface of the engaging portion 21h. And is configured to be connected (engaged).
- the vane 30 is configured to be able to slide and move in the radial direction with respect to the recess 12 a of the inner rotor 10 without being restricted by the connection angle between the vane 30 and the outer rotor piece 21.
- the outer rotor piece 21 side connected in an annular shape can be rotated in the housing 40 while maintaining the annular shape as a whole without being restricted by the connection angle with the vane 30.
- a volume chamber 63 formed by the recess 12 a and the root portion 31 a of the vane 30, and a volume chamber 61 surrounded by the inner rotor 10, the outer rotor 20 and the two adjacent vanes 30 are provided inside the inner rotor 10.
- a communication path 13 (shown by a broken line in FIG. 2) for communication is formed.
- the volume chamber 63 in the vicinity of the volume chamber 61 is configured to communicate with each other. That is, six volume chambers, each of which is a set of the volume chambers 61 to 63, are formed in a state of being partitioned from each other around the inner rotor 10.
- each component is incorporated as follows. That is, as shown in FIG. 2, the base portion 31 of the vane 30 is formed in the recess 12 a (the inner rotor 10 and the outer rotor 20 in which the six outer rotor pieces 21 are annularly connected are disposed in the housing 40. While being slid into the vane housing portion 12) along the X direction, the tip 32 of the vane 30 is fitted into the engaging portion 21h of the outer rotor piece 21 along the X direction.
- vanes 30 are similarly fitted, and the inner rotor 10 and the outer rotor 20 are connected via the vanes 30. Thereafter, a cover (not shown) is put on and the pump body 50 is closed.
- the inner rotor 10 is rotated in the arrow Q2 direction by the drive source (crankshaft)
- the outer rotor 20 is also rotated in the same arrow Q2 direction as the inner rotor 10 via the six vanes 30.
- FIG. 2 shows a state in which the rotation center R of the inner rotor 10 and the rotation center U of the outer rotor 20 are completely coincident.
- tip part 32 protrudes in the outer rotor piece 21 side by the same amount from the recessed part 12a (vane accommodating part 12). Therefore, even if the inner rotor 10 is rotated, each vane 30 is rotated and moved with the same protrusion amount, and only the outer rotor 20 is rotated. Therefore, the oil pump 100 does not exhibit a pump function as described later.
- the housing 40 holding the outer rotor 20 is moved by a predetermined amount in the Y direction (arrow Y1 direction or arrow Y2 direction).
- the rotation center U of the outer rotor 20 is configured to be eccentric in the lateral direction (arrow Y1 direction or arrow Y2 direction) relative to the rotation center R of the inner rotor 10.
- each vane 30 has a tip 32 at the outer rotor piece 21 side by an amount corresponding to the eccentricity from the recess 12 a (vane accommodating portion 12) at each rotational position along the arrow Q 2 direction. Protruding. Therefore, as the inner rotor 10 rotates, the individual vanes 30 are rotated and moved with respect to the concave portion 12a to rotate the outer rotor 20 together.
- the oil pump 100 is configured to be operated with a pump function.
- the outer rotor 20 is also rotated in the same arrow Q2 direction as the inner rotor 10 through the six vanes 30. Thereafter, based on a predetermined control operation, as shown in FIG. 8, the housing 40 holding the outer rotor 20 is moved in the direction of the arrow Y1, so that the rotation center U of the outer rotor 20 is moved with respect to the rotation center R of the inner rotor 10. Eccentric in the lateral direction (Y1 direction).
- the volume chambers 61, 62, and 63 are respectively set according to the amount of eccentricity.
- the pump is operated to change the shape (volume). That is, in the oil pump 100, the volume V1 of the volume chamber 61, the volume V2 of the volume chamber 62, and the volume V3 of the volume chamber 63 are changed (increased / decreased) according to the amount of eccentricity of the outer rotor 20 with respect to the inner rotor 10, and the pump function is exhibited. Is performed.
- the radial slide position of the distal end portion 32 (see FIG. 7) on the radially outer side of the vane 30 according to the amount of eccentricity of the outer rotor 20 with respect to the inner rotor 10 rotates and moves the outer rotor 20.
- the operation of increasing or decreasing the volume V1 is repeated by changing with the change.
- the vane 30 is The amount of protrusion of the tip 32 (see FIG. 7) is gradually increased from the recess 12a (see FIG. 7) along the radial direction.
- the distance in the circumferential direction (arrow Q direction) between the adjacent outer rotor pieces 21 surrounding one volume chamber 61 gradually increases.
- the volume V1 of the volume chamber 61 gradually increases.
- the vane 30 enters the recess 12a (see FIG. 7) along the radial direction.
- the insertion amount of the root portion 31a is gradually increased.
- the distance in the circumferential direction (arrow Q direction) between the adjacent outer rotor pieces 21 surrounding one volume chamber 61 gradually decreases. Thereby, the volume V1 of the volume chamber 61 becomes small gradually.
- the volume chamber 62 has a volume V2 as a result of the radial slide position of the distal end portion 32 on the radially outer side of the vane 30 changing with the rotational movement of the outer rotor 20 according to the amount of eccentricity of the outer rotor 20 with respect to the inner rotor 10. Repeat the operation to increase or decrease. Specifically, as each volume chamber 62 sequentially passes in the vicinity of the suction port 52 (see FIG. 8) in the direction of the arrow Q2, as the amount of protrusion of the vane 30 increases, the adjacent outer rotor pieces 21 move away from each other. And the distance between the outer rotor pieces 21 in the circumferential direction (arrow Q direction) gradually increases.
- the volume V2 of the volume chamber 62 composed of the engagement spaces 5 to 8 gradually increases. Further, as each volume chamber 62 sequentially passes in the vicinity of the discharge port 53 in the direction of the arrow Q2, as the amount of insertion of the vane 30 increases, the adjacent outer rotor pieces 21 are displaced in a direction approaching each other, and the space between the outer rotor pieces 21 is increased. The distance in the circumferential direction (arrow Q direction) gradually decreases. As a result, the volume V2 of the volume chamber 62 composed of the engagement spaces 5 to 8 gradually decreases.
- the volume chamber 63 repeats the operation of increasing / decreasing the volume V3 in the vane accommodating portion 12 of the inner rotor 10 by sliding the plurality of vanes 30 in the radial direction according to the amount of eccentricity of the outer rotor 20 with respect to the inner rotor 10. Specifically, as each volume chamber 63 sequentially passes in the direction of arrow Q2 in the vicinity of the suction port 52 (see FIG. 8), the volume V3 of the volume chamber 63 gradually increases as the protruding amount of the vane 30 increases. Become bigger. Further, as each volume chamber 63 sequentially passes in the vicinity of the discharge port 53 in the direction of the arrow Q2, the volume V3 of the volume chamber 63 gradually decreases as the insertion amount of the vane 30 increases. 9 shows a state in which the inner rotor 10 and the outer rotor 20 are rotated by about 30 degrees in the direction of the arrow Q2 with respect to FIG.
- a volume chamber 61 formed between one volume chamber 61 located between the adjacent vanes 30 and the outer rotor piece 21 engaged in the circumferential direction in this portion (engagement spaces 5 to 8).
- the volume chamber 63 in the vicinity of the volume chamber 61 are communicated with each other by the above-described notch 21f (see FIG. 6), the notch 21g (see FIG. 6), and the communication path 13 (see FIG. 7).
- the enlargement and reduction operations are synchronized with each other.
- the volume chambers 61 to 63 that are paired in terms of flow path when passing near the suction port 52 suck in the oil 1 while expanding the volume V1, the volume V2, and the volume V3 together.
- volume chambers 61 to 63 which are paired in terms of flow paths when passing near the discharge port 53, discharge the oil 1 while reducing the volume V1, the volume V2, and the volume V3 together. Note that the expansion and reduction pumping operation in which the volume chambers 61 to 63 are integrated in volume is once per rotation of the inner rotor 10.
- the amount of eccentricity of the outer rotor 20 with respect to the inner rotor 10 is adjusted to an arbitrary size depending on the movement position of the housing 40 (see FIG. 2). That is, when the amount of eccentricity is relatively small, the pump operation amount for expansion and reduction in which the volume chambers 61 to 63 are integrated in volume is relatively small, and the discharge amount of the oil 1 is relatively small. . When the amount of eccentricity is relatively large, the expansion / reduction pump operation amount in which the volume chambers 61 to 63 are integrated in volume is relatively large, and the discharge amount of the oil 1 is relatively large. .
- a series of operations from the reduced state to the expanded state and a series of operations from the expanded state to the reduced state are performed for each set of the volume chambers. It is performed sequentially with a phase shift of degrees.
- the continuous pumping operation in which the oil 1 is sucked into the pump body from the suction port 52 and discharged from the discharge port 53 is realized.
- the driving force of a drive source (not shown) rotates the inner rotor 10 and rotates the outer rotor 20 that is annularly connected to the outside via the vane 30 as the inner rotor 10 rotates.
- the six outer rotor pieces 21 periodically change the engaged state to cause the outer rotor 20 (volume chamber 62) to perform a pump operation.
- the driving force of the drive source slides (reciprocates) the vane 30 based on the eccentric state of the outer rotor 20 with respect to the inner rotor 10 when the inner rotor 10 and the outer rotor 20 are rotated together. At this time, not only a simple reciprocation of the vane 30 but also a pump operation for expanding and contracting the volume chamber 63 in the recess 12 a of the vane housing portion 12 is generated.
- the deformation motion of the movable portion (space portion: volume chambers 61 to 63) that is contained in the housing 40 and is deformed along with the rotation of the inner rotor 10 is converted into the pump operation.
- the volume chamber 63 increases the volume V1 opposite to the volume chamber 63 in the process of decreasing the volume V3. No negative factor (unnecessary work) occurs, and the synchronized volume change of the volume chambers 61 to 63 is effectively applied to the pump operation of the entire oil pump 100.
- the driving force of the driving source input to the inner rotor 10 is used for the deformation movement of the movable part (volume chambers 61 to 63). Therefore, in the oil pump 100, the mechanism in which the volume chambers 61 to 63 are integrally operated contributes to the change of the driving force of the driving source to the pump operation as much as possible to discharge the oil 1. In particular, since not only the volume chamber 61 but also the deformation motions of the volume chambers 62 and 63 are incorporated into the pump operation, the volume V1 of the volume chamber 62 and the volume V3 of the volume chamber 63 are effective for the volume V1 of the volume chamber 61. Is added to This means that the net discharge amount of oil 1 per unit rotation is increased.
- the oil pump 100 is configured as described above.
- the inner rotor 10 including the vane accommodating portions 12 (six concave portions 12a) in which each of the six vanes 30 is accommodated so as to be slidable in the radial direction, and six
- the outer rotor 20 including the six base portions 21e to which the radially outer tip portions 32 of the vanes 30 are connected, and the volume V1 varies according to the amount of eccentricity of the inner rotor 10 with respect to the outer rotor 20, thereby having a pump function.
- the pump operation of the volume chamber 62 newly provided in the outer rotor 20 can be effectively used. Therefore, the net discharge amount of the oil 1 per unit rotation in the oil pump 100 can be sufficiently increased. As a result, the pump efficiency of the oil pump 100 can be improved.
- the discharge amount of the oil 1 is efficiently increased by adding the pump operation of the volume chamber 62 on the outer rotor 20 side to the volume chamber 61 in which the discharge amount of the oil 1 is efficiently secured. be able to. Therefore, when compared with the same discharge amount, the oil pump 100 can be reduced in size by shortening the rotor width L (see FIG. 1), so that the oil pump 100 for an internal combustion engine (engine) or the like can be reduced. Mountability can be improved. In addition, since the oil pump 100 can be reduced in size, mechanical loss (mechanical loss) when the oil pump 100 is driven can be reduced, so that the load on the drive source that drives the oil pump 100 is reduced, thereby saving energy. Can be planned.
- the plurality of vanes 30 slide and move in the radial direction according to the amount of eccentricity of the inner rotor 10 with respect to the outer rotor 20, thereby changing the volume V ⁇ b> 3 in the vane housing portion 12 of the inner rotor 10.
- a volume chamber 63 having the above is further provided.
- the volume of the volume chamber 63 in the vane container 12 is obtained by the vane 30 being linearly slid in the radial direction with respect to the vane container 12.
- the oil pump 100 can be configured by incorporating it into the pumping operation for sucking and discharging the oil 1 without overlooking the change, the pump operation of the volume chamber 63 is effectively added, so that the oil pump 100 per unit rotation The discharge amount of the oil 1 can be further increased. As a result, the oil pump 100 can be further downsized. Further, since the vane 30 that is linearly slid and moved in the radial direction is used, it is not necessary to narrow the intermediate portion of each vane 30 that appears and disappears with respect to the vane accommodating portion 12 (the recess 12a).
- the volume chamber 63 changes in the direction in which the volume V3 is decreased, the volume is newly increased in the vicinity of the volume chamber 63 at the portion on the volume chamber 61 side (the volume chamber newly appears). Since no factor (unnecessary work) is generated, the volume change of the volume chambers 61 to 63 can be effectively applied to the pump operation of the entire oil pump 100.
- a suction port 52 for sucking in the oil 1 and a discharge port 53 for discharging the oil 1 are further provided.
- the vane 30 accommodated in the vane accommodating portion 12 gradually slides outward in the radial direction, whereby the volume V ⁇ b> 3 in the vane accommodating portion 12 of the inner rotor 10 gradually increases and the discharge port 53.
- the oil pump 100 is configured such that the volume V3 in the vane accommodating portion 12 of the inner rotor 10 gradually decreases as the vane 30 accommodated in the vane accommodating portion 12 gradually slides radially inward.
- the volume change of the volume V3 that repeatedly appears (increases) and disappears (decreases) in the vane accommodating portion 12 (concave portion 12a) along with the linear reciprocation of the vane 30 in the radially outward direction and the inward direction is pumped.
- the driving force of the oil pump 100 (the driving force of the inner rotor 10) is not only changed in volume of the volume chamber 61 (volume V1) and volume chamber 62 (volume V2) due to the sliding movement of the vane 30, but is also slid on the vane 30. Since it can also be converted into a volume change of the volume chamber 63 (volume V3) accompanying the movement, the driving force is not wasted and the mechanical efficiency of the oil pump 100 can be improved.
- the thickness T of the vane 30 of the base 31 accommodated in the vane accommodating portion 12 is constant.
- the vane 30 having the constant thickness T of the base 31 accommodated in the vane accommodating portion 12 can be stably slid in the radial direction without rattling the vane 30 in the vane accommodating portion 12.
- the vane 30 does not rattle during reciprocal movement, the airtightness when the volume chamber 63 repeats expansion (increase) and reduction (decrease) can be improved. Thereby, the pump efficiency of the volume chamber 63 can be maintained at a high level.
- the volume chamber 62 has a plurality of outer rotors 20 in the outer rotor 20 by changing the radial slide position of the tip 32 on the radially outer side of the vane 30 according to the eccentricity of the inner rotor 10 with respect to the outer rotor 20.
- the volume V2 of the volume chamber 62 can be changed by changing the circumferential distance between the base portions 21e. Accordingly, the circumferential distance between the plurality of base portions 21e in the outer rotor 20 can be easily changed (stretched) by appropriately using the displacement of the radial slide position of the distal end portion 32 on the radially outer side of the vane 30. it can. Thereby, the pumping function can be exhibited in the volume chamber 62 by appropriately using the driving force in the radial direction of the vane 30.
- the outer rotor 20 includes a plurality of outer rotor pieces 21 that are provided for each of the plurality of vanes 30 and each include a base portion 21e. And the outer rotor 20 is comprised so that the several outer rotor piece 21 may be arrange
- the adjacent outer rotor pieces 21 are engaged with each other in the circumferential direction (arrow Q direction) with the engagement spaces 5 to 8 constituting the volume chamber 62, and the adjacent outer rotor pieces.
- the oil pump 100 is configured such that the volume V2 of the engagement spaces 5 to 8 changes as the distance in the circumferential direction (arrow Q direction) between 21 changes. Accordingly, the engagement space 5 to 8 when the outer rotor pieces 21 are engaged with each other can be appropriately used as the volume V2, and the volume chamber 62 can exhibit a pump function of repeatedly expanding and reducing the volume V2. .
- the outer rotor piece 21 includes the first engagement piece portion 21a to the fourth engagement piece portion 21d that can be engaged in the circumferential direction with the adjacent outer rotor pieces 21 overlapping in the radial direction.
- the engagement spaces 5 and 6 that constitute a part of the volume chamber 62 have a circumferential distance that varies depending on the amount of overlap between the first engagement piece 21a and the second engagement piece 21b.
- the engagement spaces 7 and 8 constituting a part of the volume chamber 62 are changed in the circumferential distance according to the overlapping amount of the third engagement piece portion 21c and the fourth engagement piece portion 21d.
- the outer rotor 20 is configured such that the total volume V2 of the engagement spaces 5 to 8 is changed. As a result, the volume V2 of the engagement spaces 5 to 8 can be easily increased or decreased according to the amount of overlap between the first engagement piece portion 21a to the fourth engagement piece portion 21d that overlap each other.
- the chamber 62) can easily exhibit the pump function.
- the part 21g is provided on one outer rotor piece 21.
- the volume chamber 61 having the volume V1 and the volume chamber 62 having the volume V2 are communicated with each other via the cutout portion 21f and the cutout portion 21g, so that the oil 1 is supplied to the volume chamber 61 and the volume chamber when the volume chamber is enlarged. 62 can be inhaled together. Further, when the volume chamber is reduced, the oil 1 can be discharged from both the volume chamber 61 and the volume chamber 62.
- the engagement space 5 and 8 located in one side (Q1 side in FIG. 5) among the two adjacent vanes 30, and the other side (in FIG. 5) of the two adjacent vanes 30.
- the outer rotor 20 is configured such that a set of engagement spaces 5 to 8 is formed by the engagement spaces 6 and 7 positioned on the Q2 side).
- one outer rotor piece 21 is centered on one outer rotor piece 21 via, for example, the engagement spaces 5 and 8. It can be easily engaged with the outer rotor piece 21 adjacent to the side (Q1 side) and can be easily engaged with the outer rotor piece 21 adjacent to the other side (Q2 side) via the engagement spaces 6 and 7. Can do.
- the outer rotor 20 is configured such that the volume V2 gradually decreases as the distance between the outer rotor pieces 21 in the circumferential direction (arrow Q direction) gradually decreases.
- the oil film 1a is formed on the outer surface 20a of the outer rotor 20.
- the outer rotor 20 is configured so as to include a plurality of base portions 21e and a shape change that changes the volume V2 of the volume chamber 62 by changing the circumferential distance between the adjacent base portions 21e. Since the oil film 1 a is formed on the outer surface 20 a of the outer rotor 20, the annular outer rotor 20 with such a shape change can be smoothly rotated in the housing 40 of the oil pump 100. Further, the volume V2 of the volume chamber 62 can be smoothly changed by the oil film 1a.
- the plurality of vanes 30 are attached to the recesses 12a of the vane accommodating portion 12 of the inner rotor 10 so as to be slidable in the radial direction without swinging in the circumferential direction (arrow Q direction). ing.
- the individual vanes 30 can be caused to appear and disappear with respect to the vane accommodating portion 12 (recessed portion 12a) with a linear (one-dimensional) slide movement along the radial direction.
- There is no need to form a unique shape in the vane 30 such as partially narrowing the base 31 of the vane 30 that appears and disappears with respect to the vane accommodating portion 12.
- the base portion 31 is not thinned and has a constant thickness T.
- the oil pump 200 includes an inner rotor 10, an outer rotor 220, and six vanes 30 that constitute a pump element 235.
- the pump body 50 six volume chambers 261 surrounded by the inner rotor 10, the outer rotor 220, and the six vanes 30 are formed. Further, the volume V1 of the volume chamber 261 is increased or decreased according to the expansion and contraction of the volume chamber 261 accompanying the expansion and contraction (slide movement) of the vane 30 when the oil pump 200 is operated.
- the volume chamber 261 is an example of the “first volume changing portion” in the present invention.
- the outer rotor 220 has six outer rotor pieces 221 configured to be sequentially connectable (engaged) in a circumferential shape.
- the outer rotor 220 is configured to rotate in the direction of the arrow Q2 with respect to the housing 40 in a state where the outer rotor pieces 221 are connected in an annular shape within the housing 40.
- the outer rotor piece 221 includes a first engagement piece portion 221a, a second engagement piece portion 221b, and a third engagement piece portion 221c each formed in a partial arc shape. Yes.
- the outer rotor piece 221 further includes a base portion 221e extending in the axial direction (X direction), and extends in the axial direction (X direction) on the Q2 side of the first engagement piece portion 221a and the second engagement piece portion 221b.
- the root portion is connected to the base portion 221e from the Q1 side.
- a base portion extending in the axial direction (X direction) on the Q1 side of the third engagement piece portion 221c is connected to the base portion 221e from the Q2 side.
- the first engagement piece 221a and the second engagement piece 221b are on the Q1 side with respect to the base 221e
- the third engagement piece 221c is on the Q2 side with respect to the base 221e.
- These are monolithic structural parts each having a shape in which arc-shaped wings are spread.
- the outer rotor piece 221 has a uniform cross-sectional shape from the end portion on the X2 side to the end portion on the X1 side except for a notch portion 221f and a notch portion 221g described later.
- the base portion 221e is an example of the “vane connecting portion” in the present invention.
- the first engaging piece portion 221a and the second engaging piece portion 221b of the outer rotor piece 221 on the Q2 side cause the outer rotor piece 221 adjacent to the Q1 side to
- the third engagement piece 221c is engaged so as to be sandwiched from the radially outer side and the inner side.
- the third engagement piece 221c of the Q2 side (the other side) outer rotor piece 221 is sandwiched between the first engagement piece 221a and the second engagement piece 221b of the Q1 side (one side) outer rotor piece 221.
- the engaged relationship is sequentially repeated on the outer rotor pieces 221 adjacent along the Q direction. In this way, the six outer rotor pieces 221 are connected in an annular shape (circumferential shape) to form an outer rotor 220 (see FIG. 10).
- the overlap (engagement area) in the circumferential direction (arrow Q direction) between adjacent outer rotor pieces 221 is within a predetermined range (range of the length in the circumferential direction of each piece). It can be increased or decreased along the arrow Q direction. Accordingly, the outer rotor 220 incorporated in the housing 40 (see FIG. 10) increases or decreases the distance (engagement area) in the circumferential direction (arrow Q direction) within a predetermined range between the adjacent outer rotor pieces 221. Each engagement state is configured to be maintained.
- the engagement spaces 201 to 203 described below are formed between the outer rotor pieces 221 adjacent to each other in the arrow Q direction.
- One engagement space 201 capable of increasing / decreasing (extending / contracting) the volume is formed on the outer surface 3 side of the third engagement piece 221c by engagement with the combined piece 221c.
- the engagement space 201 is a space formed between the outer surface 3 of the third engagement piece 221c and the inner peripheral surface 40a (see FIG. 10) of the housing 40 facing the outer surface 3.
- one engagement space 202 is formed on the inner surface 2 side of the third engagement piece 221c so that the volume can be increased / decreased (expanded / contracted).
- This engagement space 202 is a space that is directly exposed to the inner rotor 10 (see FIG. 10) side.
- one engagement space 203 that allows the volume to be increased / decreased (expanded / contracted) at the portion where the third engagement piece 221c where the first engagement piece 221a and the second engagement piece 221b face each other is inserted. It is formed.
- the engagement spaces 201 and 202 are located on the Q1 side (one side) of the two adjacent vanes 30.
- the engagement space 203 is located on the Q2 side (the other side) of the two adjacent vanes 30.
- the engagement spaces 201 and 202 are examples of the “first engagement space” in the present invention.
- the engagement space 203 is an example of the “second engagement space” in the present invention.
- one notch 221f is formed at the connection between the base 221e and the second engagement piece 221b.
- the notch portion 221f has a predetermined length (depth) in the axial direction (X direction) from the end portion on one side (X2 side) of the base portion 221e, and a part of the second engagement piece portion 221b is in the thickness direction. It is notched in a groove shape along. Thereby, it is comprised so that the inner surface 2 side and the outer surface 3 side of the 2nd engagement piece part 221b may communicate.
- the engagement space 203 located between the 1st engagement piece part 221a and the 2nd engagement piece part 221b, the inner rotor 10, the outer rotor 220, and the two adjacent vanes 30 are used.
- the enclosed volume chamber 261 communicates with the cutout portion 221f.
- the volume of the notch 221f is as small as possible with respect to the engagement space 203 within a range where the flow of the oil 1 is easily performed.
- the notch 221f is an example of the “groove” in the present invention.
- one notch 221g is formed at the connection between the base 221e and the third engagement piece 221c.
- the notch 221g has a predetermined length (depth) in the axial direction (X direction) from one end (X2 side) of the base 221e, and a part of the third engagement piece 221c is in the thickness direction. It is notched in a groove shape along. Thereby, it is comprised so that the inner surface 2 side and the outer surface 3 side of the 3rd engagement piece part 221c may communicate.
- the volume chamber 261) is in communication with the cutout 221g.
- the volume of the notch 221g is as small as possible with respect to the engagement space 201 within a range where the flow of the oil 1 is easily performed.
- the notch 221g is an example of the “groove” in the present invention.
- the above-described engagement spaces 201, 202, and 203 form a single volume chamber 262 having a volume V ⁇ b> 2 between the outer rotor pieces 221 that are engaged with each other. That is, the total volume of the engagement spaces 201 to 203 corresponds to the volume V2.
- the engagement space 202 substantially communicates with the volume chamber 261, but here, the engagement space 202 is described separately from the volume chamber 261 as an engagement space that can be increased or decreased formed on the outer rotor 220 side.
- the volume chamber 262 is configured so that the volumes of the engagement spaces 201 to 203 are increased or decreased as the overlap (engagement area) of adjacent outer rotor pieces 221 in the circumferential direction (arrow Q direction) is increased or decreased within a predetermined range.
- the increase / decrease operations are synchronized. As a result, when the adjacent outer rotor pieces 221 are displaced away from each other, the “overlap” is reduced, and the volume V2 with the engagement spaces 201 to 203 is monotonously increased. Further, when the adjacent outer rotor pieces 221 are displaced in a direction approaching each other, the “overlap” increases, and the volume V2 is monotonously reduced. Further, the increase / decrease operation of each volume of the engagement spaces 201 to 203 plays a pump function of the outer rotor 220.
- the volume chamber 262 is an example of the “second volume changing portion” in the present invention.
- the base portion 221e of the outer rotor piece 221 is formed with an engaging portion 221h having a predetermined inner diameter and having a part in the radial direction notched in a partial arc shape (C shape).
- the engaging portion 221h extends linearly from one end portion along the axial direction of the base portion 221e to the other end portion, and penetrates the base portion 221e in the axial direction (X direction).
- the engaging portion 221h is an example of the “vane connecting portion” in the present invention.
- one volume chamber 263 having a volume V ⁇ b> 3 is formed in the vane accommodating portion 12 of the inner rotor 10 by the recess 12 a and the root portion 31 a of the vane 30.
- the volume chamber 263 is an example of the “third volume changing portion” in the present invention. Further, as the vane 30 is slidably moved relative to the recess 12a, the volume V3 of the volume chamber 263 is increased or decreased.
- the volume chamber 262 formed between one volume chamber 261 located between the adjacent vanes 30, and the outer rotor piece 221 engaged in the circumferential direction (arrow Q direction) in this part.
- the volume chamber 263 in the vicinity of the volume chamber 261 are configured to communicate with each other. That is, six volume chambers, each of which is a set of these volume chambers 261 to 263, are formed around the inner rotor 10 while being partitioned from each other.
- the volume chambers 261 and 262 are corresponding to the eccentric amount.
- And 263 are configured to perform the pump function while changing their shape (volume). That is, the volume chambers 261, 262, and 263 perform the pump function by changing the volumes V1, V2, and V3 according to the amount of eccentricity of the outer rotor 220 with respect to the inner rotor 10, respectively.
- the operation of the pump function of the volume chamber 262 will be described.
- the circumferential distance between the adjacent outer rotor pieces 221 gradually increases, so that the engagement space 201 is increased.
- the volume V2 of the volume chamber 262 consisting of ⁇ 203 gradually increases.
- the circumferential distance between the adjacent outer rotor pieces 221 is gradually reduced, so that the volume V2 of the volume chamber 262 including the engagement spaces 201 to 203 is gradually reduced.
- the adjacent outer rotor pieces 221 are engaged with each other in the circumferential direction (arrow Q direction) with the engagement spaces 201 to 203 constituting the volume chamber 262 and the circumferential direction between the adjacent outer rotor pieces 221.
- the total volume V2 of the engagement spaces 201 to 203 changes.
- the pumping operation of the volume chambers 261 and 263 is the same as the pumping operation of the volume chambers 61 and 63 described in the first embodiment.
- the volume chamber 263 is in communication with each other by the above-described notch 221f (see FIG. 13), the notch 21g (see FIG. 13) and the communication path 13 (see FIG. 14), and is expanded and contracted with each other.
- the operation is synchronized.
- the volume chambers 261 to 263 that are paired in terms of flow path suck in the oil 1 while expanding the volumes V1, V2, and V3.
- the volume chambers 261 to 263, which are paired in terms of flow paths discharge the oil 1 while reducing the volume V1, the volume V2, and the volume V3.
- the deformation motion of the movable portion (space portion: volume chambers 261 to 263) that is contained in the housing 40 and is deformed with the rotation of the pump main body is converted into the pump operation.
- the driving force of the driving source input to the inner rotor 10 is used for the deformation movement of the movable part (volume chambers 261 to 263). Therefore, also in the oil pump 200, the mechanism in which the volume chambers 261 to 263 are integrally operated contributes to the change of the driving force of the driving source to the pump operation as much as possible to discharge the oil 1. . This means that the net discharge amount of oil 1 per unit rotation is increased.
- the other structure of the oil pump 200 by 2nd Embodiment is the same as that of the said 1st Embodiment.
- the inner rotor 10 including the vane accommodating portion 12 (six concave portions 12a) in which each of the six vanes 30 is accommodated so as to be slidable in the radial direction, and the six vanes.
- the outer rotor 220 including six base portions 21e to which the respective radially outer tips 32 are connected, and the volume chamber having a pump function by changing the volume V1 according to the amount of eccentricity of the inner rotor 10 with respect to the outer rotor 220. 261 and a volume chamber 262 having a pump function by changing the volume V2 by changing the circumferential distance between the adjacent base portions 221e according to the eccentricity of the inner rotor 10 with respect to the outer rotor 220.
- the pump operation of the volume chamber 262 newly provided in the outer rotor 220 can be effectively used. Therefore, the net discharge amount of oil 1 per unit rotation in the oil pump 200 can be sufficiently increased. As a result, the pump efficiency of the oil pump 200 can be improved.
- the plurality of vanes 30 slide and move in the radial direction according to the amount of eccentricity of the inner rotor 10 with respect to the outer rotor 220, whereby the volume V3 in the vane accommodating portion 12 of the inner rotor 10 changes to change the pump function.
- a volume chamber 263 including in addition to the pumping operation of the volume chamber 261 and the volume chamber 262, the volume of the volume chamber 263 in the vane accommodating portion 12 is obtained by the vane 30 being linearly slid in the radial direction with respect to the vane accommodating portion 12.
- the oil pump 200 can be configured by incorporating it into the pumping operation for sucking and discharging the oil 1 without overlooking the change, the pumping operation of the volume chamber 263 is effectively added, so that per unit rotation of the oil pump 200 is increased. The discharge amount of the oil 1 can be further increased. As a result, the oil pump 200 can be further downsized.
- the vane 30 that is linearly slid and moved in the radial direction is used, it is not necessary to narrow the intermediate portion of each vane 30 that appears and disappears with respect to the vane housing portion 12 (recess 12a).
- volume chamber 263 undergoes a volume change in the direction of decreasing the volume V3, a negative value that newly increases the volume in the vicinity of the volume chamber 263 in the portion on the volume chamber 261 side (makes the volume chamber newly appear). Since no factor (unnecessary work) is generated, the volume change of the volume chambers 261 to 263 can be effectively applied to the pump operation of the entire oil pump 200.
- the outer rotor 220 includes a plurality of outer rotor pieces 221 that are provided for each of the plurality of vanes 30 and each include a base portion 221e. And the outer rotor 220 is comprised so that the several outer rotor piece 221 may be arrange
- the volume chamber 262 can exhibit a pumping function that repeats expansion and contraction by appropriately utilizing the separation operation (extension / contraction operation) in the circumferential direction (arrow Q direction) between the adjacent outer rotor pieces 221.
- adjacent outer rotor pieces 221 engage with each other in the circumferential direction (arrow Q direction) with the engagement spaces 201 to 203 constituting the volume chamber 262, and adjacent outer rotor pieces.
- the oil pump 200 is configured such that the volume V2 of the engagement spaces 201 to 203 is changed by changing the distance in the circumferential direction (arrow Q direction) between 221. Accordingly, the engagement space 201 to 203 when the outer rotor pieces 221 are engaged with each other can be appropriately used as the volume V2, and the volume chamber 262 can exhibit a pump function of repeatedly expanding and reducing the volume V2. .
- the outer rotor piece 221 includes the first engagement piece portion 221a to the third engagement piece portion 221c that can be engaged in the circumferential direction with the adjacent outer rotor pieces 221 overlapping in the radial direction.
- the engagement spaces 201 to 203 constituting a part of the volume chamber 262 are changed in the circumferential distance according to the overlapping amount of the first engagement piece 221a to the third engagement piece 221c.
- the outer rotor 220 is configured such that the total volume V2 of the engagement spaces 201 to 203 is changed. Accordingly, the volume V2 of the engagement spaces 201 to 203 can be easily increased or decreased in accordance with the amount of overlap between the first engagement piece 221a to the third engagement piece 221c that overlap each other.
- the chamber 262) can easily exhibit the pump function.
- the notch portion 221f that communicates the engagement space 203 constituting the volume chamber 262 and the volume chamber 261, and the engagement spaces 201 and 202 that constitute the volume chamber 262 and the volume chamber 261 are communicated.
- the notch part 221g to be provided is provided in one outer rotor piece 221.
- the volume chamber 261 having the volume V1 and the volume chamber 262 having the volume V2 are communicated with each other via the notch 221f and the notch 221g, so that the oil 1 is supplied to the volume chamber 261 and the volume chamber when the volume chamber is expanded. 262 can be inhaled together. Further, when the volume chamber is reduced, the oil 1 can be discharged from both the volume chamber 261 and the volume chamber 262.
- the engagement space 201 and 202 located in one side (Q1 side in FIG. 5) among the two adjacent vanes 30, and the other side (in FIG. 5).
- the outer rotor 220 is configured such that a set of engagement spaces 201 to 203 is formed by the engagement space 203 located on the Q2 side).
- one outer rotor piece 221 is centered on one side (Q1 side) via, for example, the engagement spaces 201 and 202.
- the configuration of an oil pump 300 according to the third embodiment of the present invention will be described with reference to FIG. 1 and FIGS.
- the moving direction of the housing 45 that houses the pump element 35 is referred to as the Y-axis direction
- the direction in which the spool member 360 that is orthogonal to the housing 45 moves is referred to as the Z-axis direction
- the rotational axis direction of the inner rotor 10 is the X-axis.
- the housing 45 is an example of the “rotor accommodating portion” in the present invention
- the spool member 360 is an example of the “cam member” in the present invention.
- the oil pump 300 As shown in FIG. 15, the oil pump 300 according to the third embodiment of the present invention is mounted on an automobile (not shown) provided with an engine 90, and pumps up oil (lubricating oil) 1 in an oil pan 91. In addition, it has a function of supplying to a movable part (sliding part) such as around the piston 92 and the crankshaft 93.
- the oil pump 300 includes a pump element 35 having a pump function, a housing 45 that houses the pump element 35 (see FIG. 1), and a pump body 80 that houses the housing 45.
- the housing 45 is an example of the “rotor accommodating portion” in the present invention.
- each volume chamber V includes volume chambers 61, 62 and 63 (see FIG. 2).
- each volume chamber V undergoes a periodic shape change as the pump element 35 rotates in the direction of the arrow Q1, thereby generating a pump function.
- the pump accommodating portion 81 is formed with a suction port 52 for sucking oil 1 and a discharge port 53 for discharging oil 1.
- a suction oil passage 95 extending from the oil pan 91 is connected to the suction port 52.
- the pump body 80 has a discharge oil passage 54 connected to the discharge port 53 of the pump housing portion 81, and the discharge oil passage 54 is an external supply oil passage that supplies oil 1 to each part of the engine 90. 96.
- the pump housing part 81 has a shape for housing the housing 45 so as to be capable of reciprocating along the Y-axis direction.
- the pump housing portion 81 has an inner surface 81a extending in the Y-axis direction on each of the Z1 side and the Z2 side
- the housing 45 is an outer surface extending in the Y-axis direction on each of the Z1 side and the Z2 side. 45b.
- the outer shape of the housing 45 is formed so that the outer surface 45 b is fitted into the pump housing portion 81 with the outer surface 45 b facing the inner surface 81 a of the pump housing portion 81.
- the housing 45 is linearly moved in the arrow Y1 direction or the arrow Y2 direction with respect to the pump housing portion 81 by sliding the outer surface 45b relative to the inner surface 81a of the pump housing portion 81. It is configured.
- the Y-axis direction is an example of the “first direction” in the present invention.
- a seal member 47 is fitted into the outer surface 45b on the Z2 side of the housing 45.
- Seal members 47 made of a rubber (resin) material are provided on the outer surface 45b on the Y1 side and the outer surface 45b on the Y2 side, respectively. Further, the seal member 47 causes the oil 1 having a relatively high pressure on the discharge port 53 side in the pump housing portion 81 to leak to the suction port 52 (suction oil passage 95) side that is a relatively low pressure region. Is configured to not.
- the pump accommodating portion 81 further has an inner side surface 81b extending in an arc shape on each of the Y1 side and the Y2 side, and the spring accommodating portion 85 is provided on the inner side surface 81b on the Y1 side. (See FIG. 15) is provided, and an opening 86 is provided on the inner side surface 81b on the Y2 side.
- a through hole 87 that penetrates the pump body 80 in the X-axis direction is formed in the center portion sandwiched between the suction port 52 and the discharge port 53 of the pump housing portion 81.
- a drive shaft (not shown) for rotating the inner rotor 10 (see FIG. 15) is inserted into the through hole 87.
- the drive shaft is fixed to the shaft hole 11 of the inner rotor 10 in a state where the inner rotor 10 is disposed in the pump housing portion 81.
- the housing 45 further has an outer surface 45c extending in an arc shape on each of the Y1 side and the Y2 side, and a seat portion 46 made of a flat surface is provided on the outer surface 45c on the Y1 side.
- a convex portion 48 is provided on the outer surface 45c on the Y2 side.
- the convex portion 48 is an example of the “cam engaging portion” in the present invention.
- the housing 45 is disposed in the pump housing portion 81 so that the convex portion 48 faces the side where the opening 86 of the pump housing portion 81 is provided (Y2 side), and the spring 45 is coiled with the spring 305. Is inserted and the seat portion 46 is pressed in the direction of the arrow Y2, and the opposite side (Y1 side) of the spring housing portion 85 from the housing 45 is sealed with a plug screw 307. Thereby, the housing 45 is always urged to the Y2 side where the opening 86 is provided by the urging force of the spring 305. Further, when the housing 45 is moved closest to the Y2 side, the tip of the convex portion 48 is configured to protrude into an oil passage portion 57 to be described later via the opening 86.
- the spring 305 is an example of the “first urging member” in the present invention.
- the inner rotor 10 has a rotation center R that is fixedly arranged. Then, when the housing 45 holding the outer rotor 20 is moved by a predetermined amount in the Y-axis direction (arrow Y1 direction or arrow Y2 direction), the rotation center U of the outer rotor 20 is relative to the rotation center R of the inner rotor 10. In particular, it is configured to be eccentric in the lateral direction (arrow Y1 direction or arrow Y2 direction). In this case, each vane 30 is protruded toward the outer rotor piece 21 by the amount corresponding to the eccentricity of the tip 32 from the recess 12a of the vane accommodating portion 12 at each rotational position (rotational angle) along the arrow Q1 direction. .
- the individual vanes 30 are rotated and moved in the direction of the arrow Q1 while appearing and retracting with respect to the recess 12a, and the outer rotor 20 is rotated in the direction of the arrow Q1.
- the internal volume is periodically changed between the minimum value and the maximum value in accordance with the shape deformation of the volume chamber V.
- the pressure in the volume chamber V decreases as the volume of the volume chamber V changes from the minimum value to the maximum value, the oil 1 is sucked, and the volume chamber changes as the volume of the volume chamber V changes from the maximum value to the minimum value.
- the sucked oil 1 is discharged.
- the oil pump 300 is configured to be operated with a pump function.
- the oil pump 300 includes a spool member 360.
- the spool member 360 is provided with a function of increasing / decreasing the eccentric amount of the rotation center U).
- the Z-axis direction is an example of the “second direction” in the present invention. This point will be specifically described below.
- the pump body 80 is formed with an oil passage portion 57 for drawing the oil 1 in the middle of the discharge oil passage 54.
- the oil passage portion 57 has a circular cross section excluding the opening 86, and a spool member 360 extending in the Z-axis direction is inserted into the oil passage portion 57.
- the oil passage portion 57 has a shape that accommodates the spool member 360 so as to be capable of reciprocating in the arrow Z1 direction or the arrow Z2 direction along the Z-axis direction.
- the direction of the arrow Z1 is an example of “one direction of the second direction” in the present invention.
- the arrow Z2 direction is an example of the “other direction of the second direction” in the present invention.
- the spool member 360 has a main body portion 361 extending in a bar shape in the Z-axis direction, and a cam shape formed in a part of the main body portion 361 near the center along the Z-axis direction. 362, a concave seat 363 formed on one end (Z1 side), and a pressure receiving surface 364 formed on the other end (Z2 side) region.
- the spool member 360 is inserted into the oil passage portion 57 so that the pressure receiving surface 364 faces the discharge oil passage 54 side, and is opposite to the oil passage portion 57 in a state where the coiled spring 306 is fitted into the seat portion 363.
- the side (Z1 side) is sealed with a plug screw 308.
- the cam-shaped portion 362 is an example of the “cam region” in the present invention.
- the spring 306 is an example of the “second biasing member” in the present invention.
- the cam-shaped portion 362 is formed so as to have a predetermined uneven shape by cutting one side surface of the main body portion 361, and an outer surface 361 a having a cylindrical shape is left in a portion other than the cam-shaped portion 362. . Further, the spool member 360 is slid with respect to the inner surface 57a in a state where the main body 361 is slid and inserted into the oil passage 57 so that the outer surface 361a faces the inner surface 57a (see FIG. 15) of the oil passage 57. As the outer side surface 361a slides, the spool member 360 is linearly moved in the arrow Z1 direction or the arrow Z2 direction with respect to the oil passage portion 57.
- the inner diameter of the oil passage portion 57 is formed by a minute amount larger than the outer diameter of the spool member 360, and the cylindrical outer surface 361a of the spool member 360 is smoother than the inner side surface 57a of the oil passage portion 57. It is configured to slide.
- the oil passage portion 57 has a pressure receiving region in which the pressure of the oil 1 discharged from the discharge port 53 acts directly in the direction of the arrow Z1 when the spool member 360 is disposed inside.
- 58a and an adjustment region 58b including the region where the cam-shaped portion 362 and the seat portion 363 are provided, and configured to allow the spool member 360 to move without directly receiving the discharge pressure of the oil 1. It is divided.
- the cam-shaped portion 362 faces the convex portion 48 of the housing 45 that projects into the adjustment region 58 b of the oil passage portion 57 through the opening 86.
- the tip of the convex portion 48 of the housing 45 is in contact with a predetermined portion of the cam-shaped portion 362 from the Y1 side by the biasing force of the spring 305.
- the oil 1 discharged from the discharge port 53 has the discharge pressure P in the pressure receiving region 58 a of the oil passage portion 57 via the discharge oil passage 54.
- the oil 1 acts on the pressure receiving surface 364 of the spool member 360, so that the spool member 360 is linearly moved in the direction of the arrow Z1.
- the housing 45 moves relative to the pump body 80 in the direction of the arrow Y1 or through the convex portion 48 that abuts the cam-shaped portion 362. It is moved in either direction of arrow Y2.
- the pump element 35 is configured such that the amount of eccentricity of the outer rotor 20 with respect to the inner rotor 10 increases and decreases as the amount of movement of the housing 45 in the Y-axis direction increases and decreases.
- the expansion and reduction pump operation amounts in which the six volume chambers V are integrated in volume are relatively relative.
- the discharge amount of the oil 1 at the same rotational speed is relatively small.
- the increase in the discharge pressure P accompanying the increase in the rotational speed becomes gentle.
- the amount of eccentricity is relatively large (for example, the state shown in FIG. 15)
- the expansion / reduction pump operation amount in which the six volume chambers V are integrated in volume is relatively large, and the same rotational speed is obtained.
- the discharge amount of the oil 1 at is relatively large. In this case, the discharge pressure P is greatly increased as the rotational speed is increased (the slope of the straight line shown in FIG. 22 is increased).
- the cam-shaped portion 362 of the spool member 360 has a surface shape such that the protrusion amount D in the Y-axis direction with respect to the convex portion 48 of the housing 45 is changed (increased or decreased) along the Z-axis direction. (Uneven shape) is formed. Accordingly, the housing 45 moves in the direction of the arrow Y1 or the direction of the arrow Y2 according to the change in the projection amount D of the cam-shaped portion 362 (the undulated state of the cam-shaped portion 362) accompanying the movement of the spool member 360 in the arrow Z1 direction. Thus, the eccentric amount of the rotation center U of the outer rotor 20 with respect to the rotation center R of the inner rotor 10 is increased or decreased.
- the cam-shaped portion 362 has a cam area 71, a cam area 72, a cam area 73, and a cam area 74 from the one end side (Z1 side) toward the other end side (Z2 side).
- the cam region 75 is connected in this order along the Z-axis direction.
- the cam areas 71, 72, and 73 are examples of the “first cam area”, the “second cam area”, and the “third cam area” in the present invention, respectively.
- the cam region 71 is flat along the Z-axis direction, and the height is a constant value along the Z-axis direction. have. Further, the cam region 72 is connected to the cam region 71 with continuity, and the height (projection amount D in the arrow Y1 direction) gradually increases as the distance from the cam region 71 in the Y2 direction increases. Is formed.
- the cam region 73 is connected to be bent in the arrow Y2 direction with respect to the end point portion on the Z2 side of the cam region 72, and has a height (projection amount D in the arrow Y1 direction) as it is further away from the cam region 72 in the Y2 direction. Is formed to gradually decrease.
- the cam region 74 is flat along the Z-axis direction while maintaining the height of the end point portion on the Z2 side of the cam region 73 (projection amount D in the arrow Y1 direction), and the height at that position is constant. It is formed to maintain the value. Note that the height of the cam region 74 is larger than the height of the cam region 71.
- the cam region 75 is connected to the end point portion on the Z2 side of the cam region 74 with continuity, and the height (the protrusion amount D in the arrow Y1 direction) increases as the cam region 75 moves away from the cam region 74 in the Y2 direction. It is formed to gradually increase.
- the cam region 71 is a region that is opposed to the convex portion 48 of the housing 45 when the discharge pressure P of the oil 1 from the discharge port 53 is in the pressure range P1 (see FIG. 15). It is.
- the cam region 72 is a region engaged with the convex portion 48 of the housing 45 when the discharge pressure P of the oil 1 from the discharge port 53 is in the pressure range P2 (see FIG. 18) larger than the pressure range P1. It is.
- the cam region 73 is a region engaged with the convex portion 48 of the housing 45 when the discharge pressure P of the oil 1 from the discharge port 53 is in the pressure range P3 (see FIG. 19) larger than the pressure range P2. It is.
- the pressure range P1, the pressure range P2, and the pressure range P3 are examples of the “first pressure range”, the “second pressure range”, and the “third pressure range” in the present invention, respectively.
- the cam region 74 is formed on the convex portion 48 of the housing 45 when the discharge pressure P of the oil 1 from the discharge port 53 is in the pressure range P4 (see FIG. 20) larger than the pressure range P3. It is an area to be engaged.
- the cam region 75 is a region engaged with the convex portion 48 of the housing 45 when the discharge pressure P of the oil 1 from the discharge port 53 is in the pressure range P5 (see FIG. 21) larger than the pressure range P4. It is. It is assumed that the relationship of pressure range P1 ⁇ pressure range P2 ⁇ pressure range P3 ⁇ pressure range P4 ⁇ pressure range P5 is satisfied.
- the spool member 360 is moved to the cam area 71, the cam area 72, the cam area 73, the cam area 74, and the cam area 75 in accordance with an increase in the discharge pressure P of the oil 1 from the discharge port 53.
- the spool member 360 is moved in the arrow Z1 direction so that the cam-shaped portions 362 are sequentially switched, the amount of movement of the housing 45 in the Y-axis direction relative to the rotation center R of the inner rotor 10 in the cam region 71 (see FIG. 15) ( While the eccentric amount of the outer rotor 20 relative to the inner rotor 10 is maintained (not changed), in the cam region 72 (see FIG. 18), the amount of movement of the housing 45 in the Y-axis direction relative to the rotation center R of the inner rotor 10 (outer rotor relative to the inner rotor 10). 20 eccentricity) is reduced.
- the inner rotor in the cam region 73 from the state in which the amount of movement of the housing 45 in the Y-axis direction relative to the rotation center R of the inner rotor 10 in the cam region 72 is reduced.
- the amount of movement of the housing 45 in the Y-axis direction with respect to the rotation center R of 10 (the eccentric amount of the outer rotor 20 with respect to the inner rotor 10) is increased (returned in the direction in which the eccentric amount increases).
- the cam region 74 see FIG.
- the amount of movement of the housing 45 in the Y-axis direction relative to the rotation center R of the inner rotor 10 is maintained (increased in the cam region 73).
- the amount of movement of the housing 45 in the Y-axis direction relative to the rotation center R of the inner rotor 10 is reduced again ( The amount of eccentricity is reduced).
- the cam region 71 is formed such that the eccentric amount of the outer rotor 20 with respect to the inner rotor 10 accompanying the movement of the housing 45 in the Y-axis direction is maintained (fixed) to the eccentric amount A1.
- the cam region 72 is formed so that the eccentric amount of the outer rotor 20 with respect to the inner rotor 10 accompanying the movement of the housing 45 in the Y-axis direction becomes (decreases) an eccentric amount A2 that is smaller than the eccentric amount A1.
- the cam region 73 is formed such that the eccentric amount of the outer rotor 20 with respect to the inner rotor 10 accompanying the movement of the housing 45 in the Y-axis direction is increased to an eccentric amount A3 that is larger than the minimum value of the eccentric amount A2.
- the eccentric amount A1, the eccentric amount A2, and the eccentric amount A3 are examples of the “first eccentric amount”, the “second eccentric amount”, and the “third eccentric amount” in the present invention, respectively.
- the cam region 74 has an eccentric amount A4 in which the eccentric amount of the outer rotor 20 with respect to the inner rotor 10 accompanying the movement of the housing 45 in the Y-axis direction is the maximum value of the eccentric amount A3 (however, the maximum value of the eccentric amount A2).
- the cam region 75 is moved to an eccentric amount A5 in which the eccentric amount of the outer rotor 20 with respect to the inner rotor 10 accompanying the movement of the housing 45 in the Y-axis direction is smaller than the eccentric amount A4. It is formed to be reduced.
- the cam region 71, the cam region 72, the cam region 73, the cam region 74, and the cam region 75 are provided so as to be continuous, and the convex portion 48 of the housing 45 is formed in the arrow Z1 direction of the spool member 360. Along with the movement, it is moved in the Y axis direction (arrow Y1 direction or arrow Y2 direction) by sequentially sliding along the cam region 71, the cam region 72, the cam region 73, the cam region 74, and the cam region 75. It is configured as follows.
- the cam region 71 of the spool member 360 is By moving linearly to a position corresponding to the convex portion 48, the housing 45 is linearly moved to the first eccentric position in the Y-axis direction so that the eccentric amount A1 that is the maximum eccentric amount is maintained. It is configured. Further, in the pressure range P2 (see FIG. 18), the cam region 72 of the spool member 360 is linearly moved to a position where the cam region 72 engages with the convex portion 48 of the housing 45, whereby the housing 45 is moved in the Y-axis direction.
- the cam region 73 of the spool member 360 is linearly moved to a position where it engages with the convex portion 48 of the housing 45, whereby the housing 45 is moved in the Y-axis direction. It is configured to be linearly moved to the 3 eccentric position and changed to an eccentric amount A3 larger than the minimum value of the eccentric amount A2.
- the cam region 74 of the spool member 360 is linearly moved to a position where the cam region 74 engages with the convex portion 48 of the housing 45, whereby the housing 45 is moved in the Y-axis direction. It is configured to be moved linearly to the 4 eccentric position and maintained at the eccentric amount A4 which is the maximum eccentric amount of the eccentric amount A3.
- the cam region 75 of the spool member 360 is linearly moved to a position where the cam region 75 engages with the convex portion 48 of the housing 45, whereby the housing 45 is moved in the Y-axis direction. It is configured to be linearly moved to the 5 eccentric position and changed to an eccentric amount A5 smaller than the eccentric amount A4.
- the suction port 52 (suction oil passage 95) in the pump housing portion 81 is connected to the cam-shaped portion 362 of the spool member 360 via the opening 86 in the Y2 side region. Is communicated with the adjustment region 58b provided with Therefore, during operation of the pump element 35, at least a part of the oil 1 sucked into the suction port 52 through the opening 86 is drawn into the cam-shaped portion 362 (cam region 71 to cam region 75) of the spool member 360. It is.
- the oil 1 having a pressure lower than the discharge pressure P is moved around the cam-shaped portion 362 (adjustment region 58b).
- the cam region 71 to the cam region 75 are configured to be easily pulled in and to be lubricated.
- the spool member 360 has a through-hole 365 that penetrates the inside (bottom) of the seat 363 in the Z-axis direction so that the side where the spring 306 is provided communicates with the cam region 71 (cam-shaped portion 362). Is formed.
- each vane 30 In the state where the rotation center R of the inner rotor 10 and the rotation center U of the outer rotor 20 are completely coincident with each other, each vane 30 has the tip 32 on the outer rotor piece 21 side by the same amount from the recess 12a (the vane housing portion 12). Protruding. Therefore, even if the inner rotor 10 is rotated, each vane 30 is rotated and moved with the same protrusion amount, and only the outer rotor 20 is rotated. Therefore, the oil pump 300 does not exhibit a pump function.
- the oil pump 300 has the following characteristics (discharge pressure characteristics of the oil 1 with respect to the rotational speed of the inner rotor 10).
- the characteristic of the discharge pressure (vertical axis) of the oil 1 discharged from the pump body 80 (discharge oil passage 54) with respect to the rotational speed (horizontal axis) of the engine 90 (crankshaft 93) is shown.
- FIG. 22 shows characteristics (discharge pressure characteristics) of a conventional oil pump as a comparative example.
- the spool member 360 has the cam region 71 opposed to the convex portion 48 of the housing 45 as shown in FIG. The In this case, even if the rotation speed of the engine 90 (crankshaft 93) is increased and the discharge pressure P of the oil 1 from the discharge port 53 is increased, the spool member 360 is moved in the direction of the arrow Z1 along the Z-axis direction. Since the flat cam region 71 is only moved in the arrow Z1 direction, the amount of movement of the convex portion 48 in the Y-axis direction does not change.
- the discharge pressure characteristic when the housing 45 is maintained at the eccentric amount A1 has a shape like the characteristic G1 in FIG.
- a straight line having a slope of the characteristic G1 corresponds to a maximum eccentricity line in the oil pump 300.
- the range of the characteristic G1 corresponds to the pressure range P1 at the discharge pressure P.
- the housing 45 is changed (decreased) from the eccentric amount A1 (a constant value) to the eccentric amount A2.
- the discharge pressure characteristic in this case shows a shape like the characteristic G2 in FIG. Further, the range of the characteristic G2 corresponds to the pressure range P2 at the discharge pressure P.
- the amount of eccentricity of the outer rotor 20 with respect to the inner rotor 10 increases as the amount of protrusion D in the direction of the arrow Y1 decreases. Accordingly, the housing 45 is changed (increased) to the eccentric amount A3 that is larger than the maximum value of the eccentric amount A2 after the maximum value of the eccentric amount A2.
- the discharge pressure characteristic in this case shows a shape like a characteristic G3 in FIG. Further, the range of the characteristic G3 corresponds to the pressure range P3 at the discharge pressure P.
- the discharge pressure characteristic in this case shows a shape like a characteristic G4 in FIG.
- the range of the characteristic G4 corresponds to the pressure range P4 at the discharge pressure P.
- the slope of the characteristic G4 is smaller than the slope of the characteristic G1. That is, in the housing 45, the eccentric amount is reduced to the eccentric amount A4 than the eccentric amount A1, and the pump capacity (net discharge amount per one rotation) is reduced. That is, a straight line having a slope of the characteristic G4 (a broken line obtained by extending the characteristic G4) corresponds to an eccentricity line between the maximum and minimum in the oil pump 300.
- the discharge pressure characteristic in this case shows a shape like a characteristic G5 in FIG. Note that a straight line having a slope of the characteristic G5 (a broken line obtained by extending the characteristic G5) corresponds to a minimum eccentricity line in the oil pump 300.
- the range of the characteristic G5 corresponds to the pressure range P5 at the discharge pressure P.
- the oil pump 300 has a discharge pressure characteristic that connects the characteristics G1 to G5 indicated by the thick solid line.
- the discharge pressure P of the oil 1 is increased with the increase in the rotation speed of the engine 90 (crankshaft 93) in the section where the rotation speed of the engine 90 is up to about 2900 rotations / minute.
- the amount of eccentricity of the housing (rotor accommodating portion) in this case, the amount of eccentricity A1 is not changed. Therefore, as shown in FIG. 22, the characteristic that the graph is extended until the rotational speed of the engine 90 reaches a position of about 2900 revolutions / minute with the same inclination as the characteristic G1 in the oil pump 300 (see FIG. 15). H1 is shown.
- the housing (rotor accommodating portion) is moved in one direction based on the discharge pressure P.
- the amount of eccentricity of the housing (rotor housing) is immediately reduced from the maximum amount of eccentricity A1 to the minimum amount of eccentricity A5 (A1> A5). Therefore, at about 2900 revolutions / minute, the characteristic H2 having a smaller inclination than the characteristic H1 is traced.
- the characteristic H2 has the same inclination as that of the characteristic G5 in the oil pump 300 (see FIG. 15) and extends to a position where the rotational speed of the engine 90 is about 2900 revolutions / minute.
- the oil pump of the comparative example has a discharge pressure characteristic in which the characteristic H1 (maximum eccentricity line) and the characteristic H2 (minimum eccentricity line) indicated by the thick broken line are connected.
- operation points S1 to S4 for supplying the oil 1 with a predetermined hydraulic pressure are set according to the rotational speed of the engine 90. Yes.
- the discharge pressure characteristics (characteristics G1 to G5) that satisfy the supply pressure of the oil 1 required at the operation points S1 to S4 are realized.
- the discharge pressure characteristics (characteristics H1 to H2) satisfy this point.
- the required discharge pressure characteristic only needs to pass near the upper part of each of the operation points S1 to S4. In particular, when attention is paid to the operation point S3 (about 4000 rpm) that is the medium speed rotation region of the engine 90.
- the discharge pressure P required in the characteristic G4 portion of the oil pump 300 is at least satisfied.
- the oil pump of the comparative example since the oil pump of the comparative example has only two kinds of inclinations of the characteristic H1 and the characteristic H2, it satisfies the required pressure at the operating point S3 (about 4000 rpm), but this pressure is much higher.
- the oil 1 is supplied at a discharge pressure P (part of the characteristic H2) exceeding 1.
- the oil pump 300 is configured so as to satisfy the required pressure of the oil 1 at the operation point S3 by having the characteristics G2 to H4 and not to generate an excessive discharge pressure P unlike the oil pump of the comparative example. .
- the change from the characteristic G2 to the characteristic H4 follows the uneven shape of the cam-shaped portion 362 (see FIG. 15) when the spool member 360 (see FIG.
- the housing 45 is realized by reversibly moving the pump body 80 in the two directions of the arrow Y1 direction and the arrow Y2 direction.
- the oil in the third embodiment responds to a change from the characteristic H1 (characteristic obtained by extending the characteristic G1 to the medium speed rotation range) to the characteristic H2 (characteristic obtained by extending the characteristic G5 to the medium speed rotation range) in the oil pump of the comparative example.
- the fact that the pump 300 has a section between the characteristic G2 and the characteristic G4 that is bent with a valley between the characteristic G1 and the characteristic G5 means that the pump element 35 (see FIG. 15) is useless (excessive) even at the same rotational speed.
- the discharge pressure characteristic follows a change in the opposite direction. That is, the discharge pressure P is changed in the order of characteristics G5, G4, G3, G2, and G1.
- the Y-axis direction of the housing 45 (in the direction of the arrow Y1 or the arrow) according to the change in the protrusion amount D of the cam-shaped portion 362 when the spool member 360 is linearly moved in the direction of the arrow Z1.
- the housing 45 in accordance with the characteristics of the eccentric amount of the outer rotor 20 relative to the inner rotor 10 due to the movement in the Y2 direction) and the change in the protruding amount D of the cam-shaped portion 362 when the spool member 360 is linearly moved in the arrow Z2 direction.
- the characteristic of the eccentric amount of the outer rotor 20 with respect to the inner rotor 10 due to the movement in the X direction has a hysteresis difference.
- the spool member 360 is moved in the arrow Z1 direction according to the discharge pressure P of the oil 1. It is moved linearly, and the tip of the convex portion 48 of the housing 45 is slid in the order of the cam regions 72, 73 and 74.
- the discharge pressure characteristic follows the path of the characteristic G2, the characteristic G3, and the characteristic G4 so as to extend from the left side to the right side.
- the discharge pressure characteristic follows the path of the characteristic G41, the characteristic G31, and the characteristic G21 so as to extend from the right side to the left side in FIG.
- the discharge pressure characteristic is not switched from the characteristic G2 to the characteristic G3 and from the characteristic G3 to the characteristic G4 unless a relatively high rotational speed is reached.
- the discharge pressure characteristics are not switched from the characteristic G41 to the characteristic G31 and from the characteristic G31 to the characteristic G21 unless the engine speed reaches a lower speed than when the engine speed is increasing.
- the predetermined discharge pressure P vertical axis
- the discharge pressure P is maintained up to a rotational speed R2 (R2 ⁇ R1) lower than the rotational speed R2 at which the discharge pressure P is obtained when the engine 90 is increased, and the rotational speed is decreased to a rotational speed lower than the rotational speed R2. In this stage, the discharge pressure P is reduced.
- the reason for this is as follows.
- the cam region 72 of the spool member 360 will be described as an example. As shown in FIG. 15, the cam region 72 formed with a predetermined inclination angle in the direction of increasing the projection amount D from the Z1 side to the Z2 side.
- the spool member 360 is linearly moved in the arrow Z1 direction to When the tip surface of the cam region 72 is slid from the Z1 side (the side with the small protrusion amount D) to the Z2 side (the side with the large protrusion amount D), the spool member 360 has the arrow Z2 of the spring 306.
- the spool member 360 is linearly moved in the direction of the arrow Z2, and the inclined surface of the cam region 72 is changed from the Z2 side (the side with the larger projection amount D) to the Z1 side (the projection amount D is smaller).
- the biasing force of the spring 305 is applied to the inclined surface of the cam region 72 via the tip of the convex portion 48 by the pressing force F1 acting in the arrow Z2 direction of the spring 306.
- a load F1-F2 (acting in the direction of the arrow Z2) is applied by subtracting the spring load (pressing force) F2 that is decomposed in the direction of the arrow Z1 based on the inclination angle of the cam region 72 when pressed in the direction of the arrow Y2. Therefore, in order to move the spool member 360 linearly in the direction of the arrow Z2, only a pressing force smaller than the load F1-F2 acting in the direction of the arrow Z2 acts on the pressure receiving surface 364 in the direction of the arrow Z1. Good.
- the spool member 360 follows the frequent vertical fluctuations of the discharge pressure P. Is moved frequently in the directions of the arrows Z1 and Z2, and the chattering phenomenon in which the reciprocating movement of the housing 45 along the Y-axis direction is frequently repeated does not occur.
- the oil pump 300 in the third embodiment is configured as described above.
- the spool member 360 includes a cam-shaped portion 362 provided to increase or decrease the amount of eccentricity of the outer rotor 20 with respect to the inner rotor 10 by moving the housing 45 in the Y-axis direction (the direction of the arrow Y1 or the direction of the arrow Y2). Is provided.
- the housing 45 is moved in the Y-axis direction via the cam-shaped portion 362 provided in the spool member 360 in accordance with the linear movement of the spool member 360 in the arrow Z1 direction according to the discharge pressure P of the oil 1.
- the amount of eccentricity of the outer rotor 20 with respect to the inner rotor 10 can be easily changed by increasing or decreasing it. Therefore, in the oil pump 300, the amount of eccentricity of the outer rotor 20 relative to the inner rotor 10 can be increased or decreased only by movement in one direction (the direction of the arrow Z1), so that it depends on the discharge pressure P of the oil 1 (the rotational speed of the engine 90). Therefore, there is no need to switch the operation position of the oil pressure, and as a result, there is no need to provide a hydraulic direction switching valve or the like, so that the configuration of the oil pump 300 can be further simplified.
- the housing 45 includes a convex portion 48 disposed so as to face the cam-shaped portion 362 of the spool member 360, and the cam-shaped portion 362 of the spool member 360 is the convex portion 48 of the housing 45.
- the protrusion amount D with respect to the angle changes along the Z-axis direction.
- the housing 45 is moved in the Y-axis direction (arrow Y1 direction or arrow Y2 direction) in accordance with the change in the protrusion amount D of the cam-shaped portion 362 accompanying the movement of the spool member 360 in the arrow Z1 direction, and the outer rotor with respect to the inner rotor 10. It is configured so that the amount of eccentricity of 20 is increased or decreased.
- the cam mechanism configured by the cam-shaped portion 362 of the spool member 360 and the convex portion 48 of the housing 45 is effectively used, and the cam-shaped portion 362 protrudes as the spool member 360 moves in the arrow Z1 direction.
- the amount of eccentricity of the outer rotor 20 with respect to the inner rotor 10 can be increased or decreased by directly following the change in the amount D.
- the cam-shaped portion 362 of the spool member 360 is a cam region that is disposed to face the convex portion 48 of the housing 45 when the discharge pressure P of the oil 1 from the discharge port 53 is in the pressure range P1.
- a cam region 72 that engages the convex portion 48 of the housing 45 when the discharge pressure P is in the pressure range P2 larger than the pressure range P1, and a pressure range P3 in which the discharge pressure P is larger than the pressure range P2.
- at least a cam region 73 that engages the convex portion 48 of the housing 45.
- the spool member 360 is moved to an arrow so that the cam shape portion 362 of the spool member 360 is sequentially switched to the cam region 71, the cam region 72, and the cam region 73.
- the amount of movement of the housing 45 in the Y-axis direction relative to the rotation center R of the inner rotor 10 in the cam region 72 and the amount of eccentricity of the outer rotor 20 relative to the inner rotor 10 are reduced.
- the discharge pressure P of the oil 1 is changed from the pressure range P1 to the pressure range P2, and the pressure range P2 with respect to the cam region 71 corresponding to the case where the discharge pressure P of the oil 1 from the discharge port 53 is in the pressure range P1
- the cam-shaped portion 362 of the spool member 360 is sequentially switched from the cam region 71 to the cam region 72 and from the cam region 72 to the cam region 73 along the arrow Z1 direction.
- the switching to the cam regions 71 to 73 accompanying the movement of the spool member 360 in the arrow Z1 direction can cause both a decrease and an increase in the eccentric amount of the outer rotor 20 with respect to the inner rotor 10, so that the oil pump 300
- desired discharge pressure characteristics can be easily generated.
- the cam region 71 is formed so that the eccentric amount of the outer rotor 20 with respect to the inner rotor 10 accompanying the movement of the housing 45 in the Y-axis direction becomes the eccentric amount A1, and the housing 45 in the Y-axis direction is formed.
- the cam region 72 is formed so that the amount of eccentricity of the outer rotor 20 with respect to the inner rotor 10 is smaller than the amount of eccentricity A1, and the eccentricity of the outer rotor 20 with respect to the inner rotor 10 with the movement of the housing 45 in the Y-axis direction is formed.
- the cam region 73 is formed so that the amount becomes an eccentric amount A3 larger than the minimum value of the eccentric amount A2.
- the pump capacity is adjusted to be smaller than the pressure range P1 when the discharge pressure P of the oil 1 is within the pressure range P2.
- the pump capacity can be adjusted to be larger than the pressure range P2 and smaller than the pressure range P1.
- the cam region 72 is provided so that the eccentric amount of the outer rotor 20 with respect to the inner rotor 10 decreases from the eccentric amount A1 to the eccentric amount A2 toward the cam region 73, and the inner rotor 10 moves toward the cam region 74.
- the cam region 73 is provided so that the amount of eccentricity of the outer rotor 20 relative to the amount increases from the amount of eccentricity A2 to the amount of eccentricity A3.
- the amount of eccentricity of the outer rotor 20 with respect to the inner rotor 10 accompanying the movement of the housing 45 in the Y-axis direction can be easily increased.
- the cam region 71, the cam region 72, and the cam region 73 are provided so as to be continuous, and the convex portion 48 of the housing 45 is at least a cam according to the movement of the spool member 360.
- the convex portion 48 is engaged so as to follow the cam shape (inclined shape) of the cam shape portion 362 (cam region 72 and cam region 73).
- the outer rotor with respect to the inner rotor 10 in the cam region 72 is based on the cam region 71 corresponding to the case where the discharge pressure P of the oil 1 from the discharge port 53 is in the pressure range P1.
- the amount of eccentricity 20 can be reduced smoothly, and the amount of eccentricity of the outer rotor 20 relative to the inner rotor 10 can be increased smoothly from the reduced state in the cam region 73.
- the cam region 71 of the spool member 360 is linearly moved to a position corresponding to the convex portion 48 of the housing 45 in the pressure range P1, so that the housing 45 is moved in the first direction in the Y-axis direction. It is configured to be moved linearly to the eccentric position so that the eccentric amount A1 is the maximum eccentric amount. Further, in the pressure range P2, the cam region 72 of the spool member 360 is linearly moved to a position where the cam region 72 engages with the convex portion 48 of the housing 45, so that the housing 45 is linearly moved to the second eccentric position in the Y-axis direction. So that the eccentric amount A2 is smaller than the eccentric amount A1.
- the cam region 73 of the spool member 360 is linearly moved to a position where the cam region 73 engages with the convex portion 48 of the housing 45, whereby the housing 45 is linearly moved to the third eccentric position in the Y-axis direction.
- the eccentric amount A3 is larger than the minimum value of the eccentric amount A2. Accordingly, the housing 45 is moved to any one of the first eccentric position, the second eccentric position, and the third eccentric position corresponding to each of the pressure range P1, the pressure range P2, and the pressure range P3, and the outer rotor 20 with respect to the inner rotor 10 is also detected. Can be appropriately adjusted to the amount of eccentricity A1, the amount of eccentricity A2, and the amount of eccentricity A3. Therefore, it is possible to obtain the oil pump 300 that can accurately exhibit the required discharge pressure characteristics.
- a spring 305 that urges the housing 45 toward the spool member 360 in the arrow Y2 direction is provided.
- the spring 305 attaches the housing 45 to the spool member 360 side in the arrow Y2 direction.
- the housing 45 can be moved in the Y-axis direction while appropriately following the cam shape (uneven shape) of the cam-shaped portion 362 of the spool member 360.
- a spring 306 that urges the spool member 360 in the arrow Z2 direction so as to go toward the discharge oil passage 54 (position on the discharge port 53 side) is provided.
- the Y axis direction of the housing 45 (the arrow Y1 direction or the arrow Y2) according to the change in the protrusion amount D of the cam-shaped portion 362 when the spool member 360 is linearly moved in the arrow Z1 direction.
- Characteristic of the eccentric amount of the outer rotor 20 relative to the inner rotor 10 due to movement in the direction transition to characteristics G2, G3, and G4 in FIG. 23), and the cam shape when the spool member 360 is linearly moved in the arrow Z2 direction.
- the characteristic of the eccentric amount of the outer rotor 20 with respect to the inner rotor 10 due to the movement of the housing 45 in the X direction according to the change in the protrusion amount D of the portion 362 (the transition to the characteristics G41, G31 and G21 in FIG. 23) is a hysteresis difference. Have.
- the characteristic of the eccentric amount of the rotation center U of the outer rotor 20 with respect to the inner rotor 10 depends on the moving direction of the spool member 360.
- the spool member 360 moves linearly in the directions of the arrows Z1 and Z2 following the frequent vertical fluctuations in the discharge pressure P, and the housing 45 moves in the Y-axis direction based on this movement. It is possible to avoid the occurrence of a phenomenon (chattering phenomenon) in the oil pump 300 in which the reciprocating operation is repeated frequently. Therefore, even when the discharge pressure P of the oil 1 from the discharge port 53 repeatedly fluctuates up and down at short time intervals, the eccentric amount of the outer rotor 20 with respect to the inner rotor 10 does not fluctuate little by little, so that the oil 1 can be stabilized. Can be discharged.
- the pump housing portion 81 of the pump body 80 is provided with an opening 86 that opens to the oil passage portion 57.
- the oil pump 300 is configured such that at least part of the oil 1 sucked into the suction port 52 through the opening 86 is drawn into the cam-shaped portion 362 (cam region 71 to cam region 75) of the spool member 360. .
- the housing 45 is moved in the Y-axis direction via the cam-shaped portion 362 provided on the spool member 360, the oil 1 whose pressure is lower than the discharge pressure P is easily drawn into the cam-shaped portion 362.
- the cam operation for moving the housing 45 in the Y-axis direction by the spool member 360 is made smooth. It can be carried out.
- a smooth discharge pressure characteristic can be obtained while accurately following the discharge pressure P of the oil 1 from the discharge port 53.
- the oil pump 400 according to the fourth embodiment of the present invention includes a spool member 460 as shown in FIG.
- the spool member 460 is an example of the “cam member” in the present invention.
- the cam-shaped portion 462 of the spool member 460 includes a cam region 71, a cam region 72, and a cam region 71 from the one end side (Z1 side) to the other end side (Z2 side).
- the cam region 473 and the cam region 475 are configured to be connected in this order along the Z-axis direction. That is, the cam region 473 is connected to the cam region 475 without providing the cam region 74 (see FIG. 15) parallel to the Z-axis direction like the spool member 360 (see FIG. 15). Therefore, the cam region 473 is slightly longer than the cam region 73 (see FIG.
- cam region 475 is the cam region while maintaining the same inclination as there is no cam region 74 (see FIG. 15). It extends to the 473 side.
- the cam-shaped portion 462 is an example of the “cam region” in the present invention
- the cam region 473 is an example of the “third cam region” in the present invention.
- the oil pump 400 has characteristics as shown in FIG. 25 (discharge pressure characteristics of the oil 1 with respect to the rotation speed of the inner rotor 10).
- the characteristics G1 and characteristics G2 in the cam area 71 and the cam area 72 due to the movement of the spool member 460 in the arrow Z1 direction are the same as those in the case of the oil pump 300. Further, when the rotational speed of the engine 90 (see FIG. 24) exceeds about 3600 revolutions / minute and the discharge pressure P exceeds the maximum value of the pressure range P2, the spool member 460 moved in the arrow Z1 direction has a convex portion. The engagement position with respect to 48 is switched from the cam region 72 to the cam region 473.
- the amount of eccentricity of the outer rotor 20 with respect to the inner rotor 10 is increased as the protrusion amount D in the direction of the arrow Y1 decreases, and the discharge pressure characteristic shows a shape like the characteristic G6.
- the rotational speed of the engine 90 exceeds about 3900 revolutions / minute and the discharge pressure P exceeds the maximum value of the pressure range P3
- the spool member 460 moved in the direction of the arrow Z1 is engaged with the convex portion 48. Is switched from the cam area 473 to the cam area 475.
- the eccentric amount of the outer rotor 20 with respect to the inner rotor 10 is decreased again with the increase of the protruding amount D in the direction of the arrow Y1, and the discharge pressure characteristic shows a shape like the characteristic G7.
- the oil pump 400 has a discharge pressure characteristic that connects the characteristics G1, G2, G6, and G7 indicated by the thick solid lines.
- the pump element 35 has a characteristic that satisfies the required pressure of the oil 1 at a predetermined operating point S3 without generating useless (excessive) hydraulic pressure even at the same rotation speed. Means. Therefore, the pump power can be reduced by the amount that no unnecessary (excessive) hydraulic pressure is generated in the oil pump 400. Reduction in pump power also contributes to reduction in load (loss) of the engine 90, leading to improvement in fuel consumption rate.
- the rotation speed of the engine 90 see FIG.
- the discharge pressure characteristic follows a change in the opposite direction. That is, the discharge pressure P is changed in the order of the characteristics G7, G6, G2, and G1.
- the other structure of the oil pump 400 by 4th Embodiment is the same as that of the said 3rd Embodiment.
- the housing 45 is moved in the Y-axis direction via the cam-shaped portion 462 provided in the spool member 460 in accordance with the linear movement of the spool member 460 in the arrow Z1 direction according to the discharge pressure P of the oil 1.
- the amount of eccentricity of the outer rotor 20 with respect to the inner rotor 10 can be easily changed by increasing or decreasing it. Therefore, for example, a plurality of systems of hydraulic circuits, hydraulic direction switching valves, and the like are provided to switch the method of applying oil pressure to the housing 45 (operation position) in accordance with the discharge pressure P of the oil 1 (the rotational speed of the engine 90).
- the inner rotor is moved linearly in the Z-axis direction according to the discharge pressure P of the oil 1, and the housing 45 is moved in the Y-axis direction along with the linear movement in the arrow Z1 direction.
- the spool member 460 that increases or decreases the amount of eccentricity of the outer rotor 20 with respect to 10 can also generate a desired discharge pressure characteristic in the oil pump 400 as in the case where a hydraulic direction switching valve or the like is provided.
- the configuration of 400 can be further simplified. The remaining effects of the fourth embodiment are similar to those of the aforementioned third embodiment.
- vanes 30 are arranged at equal angular intervals (60 degree intervals) between the inner rotor 10 and the outer rotor 20 (220). 400) is shown as an example, but the present invention is not limited to this.
- the number of vanes 30 may be other than 6, for example, 4 (90 degree intervals), 5 (72 degree intervals), 8 (45 degree intervals), or 9 (40 degree intervals).
- the number of outer rotor pieces constituting the outer rotor is also changed according to the number of vanes 30.
- the outer rotor piece 21 is provided with the notches 21f and 21g so that the volume portions 62 and 61 communicate with each other.
- the outer rotor piece 221 is notched.
- a communication hole may be provided in the outer rotor piece.
- the outer rotor piece 521 may be configured as in the modification shown in FIG.
- a communication hole 501 that penetrates the second engagement piece portion 21b in the thickness direction is provided at a connection portion between the base portion 21e and the second engagement piece portion 21b, and the first engagement piece portion 21a and the fourth engagement piece.
- a communication hole 502 that penetrates the fourth engagement piece 21d in the thickness direction may be provided at an end facing the portion 21d in the axial direction (X direction).
- the communication holes 501 and 502 are an example of the “hole” in the present invention.
- the crankshaft 93 of the internal combustion engine (engine 90) is used as the drive source of the inner rotor 10
- an electric motor may be used as a drive source for the oil pump (inner rotor).
- the discharge rate of the oil pump 100 (200, 300, 400) may be variable according to the eccentricity of the outer rotor 20 with respect to the inner rotor 10 with the rotation speed of the electric motor being constant, and the machine of the outer rotor 20 accompanying this eccentricity.
- the discharge amount of the oil pump 100 (200, 300, 400) is adjusted more finely with respect to the required discharge amount by further changing the rotation speed of the electric motor. May be.
- the discharge amount corresponding to the eccentric amount is obtained by translating the housing 40 (45) with respect to the inner rotor 10 having the rotation center R fixed inside the pump body 50 (80).
- the oil pump 100 200, 300, 400
- the present invention is not limited to this.
- a rotation fulcrum is provided on one side of the housing 40 (45), and the other side of the housing 40 (45) is rotated by a predetermined angle around the rotation fulcrum, thereby decentering the outer rotor 20 with respect to the inner rotor 10.
- the oil pump may be configured to generate.
- the present invention is not limited to this. That is, by configuring the rotation center R of the inner rotor 10 to be movable, the inner rotor 10 is decentered with respect to the fixed housing 40, and the oil pump 100 (200 ) May be configured.
- the housing 45 is decentered in the Y-axis direction (arrow Y1 direction or arrow Y2 direction) with respect to the inner rotor 10 with the rotation center R fixed.
- the invention is not limited to this. That is, by configuring the rotation center R of the inner rotor 10 to be movable in the Y-axis direction, the rotation center R of the inner rotor 10 is decentered with respect to the rotation center U of the fixed housing 45, and the arrow Z1 of the spool member 360 is
- the oil pump 300 (400) may be configured such that the discharge pressure is changed according to the amount of forward and reverse eccentricity of the inner rotor 10 accompanying the movement in the direction.
- the housing 45 is provided with respect to the cam-shaped portion 362 (462) in which the spool members 360 (460) have different inclination angles and the plurality of cam regions are continuously connected.
- the housing 45 is configured to move forward and backward in the Y-axis direction in a state where the tip of the convex portion 48 is in contact.
- the present invention is not limited to this.
- a cam groove having a projection amount D similar to that of the cam-shaped portion 362 is formed in the spool member, and the cam groove is fitted into a portion corresponding to the convex portion 48 of the housing 45 (rotor accommodating portion).
- the engagement state between the engagement pin of the rotor accommodating portion and the cam groove of the spool member is utilized.
- You may comprise so that the amount of eccentricity of the outer rotor 20 with respect to the inner rotor 10 may be increased / decreased while moving a rotor accommodating part to a Y-axis direction (arrow Y1 direction or arrow Y2 direction).
- the convex portion 48 of the housing 45 abuts in the direction of the arrow Y2 by the urging force of the spring 305 against the cam-shaped portion 362 (462) of the spool member 360 (460).
- the housing 45 (convex portion 48) is pushed from the cam-shaped portion 362 (462) and pushed out in the arrow Y1 direction along with the linear movement of the spool member 360 (460) in the arrow Z1 direction.
- the oil pump 300 (400) is configured to be included has been shown, the present invention is not limited to this.
- an engagement method (engagement mechanism) between the spool member and the rotor accommodating portion, for example, it includes an operation in which the rotor accommodating portion is pulled out in the arrow Y1 direction along with the linear movement of the spool member in the arrow Z1 direction.
- An oil pump may be configured as described above.
- the cam member 362 including the cam regions 71 to 75 is provided on the spool member 360.
- the cam member 462 including the cam regions 71, 72, 473, and 475 is provided.
- the cam shape (uneven shape) of the cam region may be other than the above.
- the cam shape of the cam region can be appropriately changed according to the operating point required for a device (such as an automobile) to which hydraulic pressure is supplied.
- the spool member 360 (460) is capable of reciprocating in the Z-axis direction orthogonal to the Y-axis direction with respect to the housing 45 capable of reciprocating in the Y-axis direction in the pump body 80.
- the linear movement direction of the spool member 360 corresponding to the discharge pressure P of the oil 1 only needs to intersect the movement direction of the housing 45.
- the pump body 80 and the internal oil path may be configured such that the spool member 360 is linearly moved along the X-axis direction in which the rotation axis of the inner rotor 10 extends.
- the oil pump 100 (200) is configured by rotating the inner rotor 10 in the direction of the arrow Q2 to rotate the outer rotor 20 (220) in the same direction.
- the present invention is not limited to this.
- oil pump 100 (200) may be configured by rotating inner rotor 10 in the direction of arrow Q1 opposite to the direction of arrow Q2. That is, since the vane 30 repeats linear protrusions and recesses along the radial direction with respect to the inner rotor 10, the rotation direction of the inner rotor 10 is not questioned. However, when the inner rotor 10 is rotated in the direction of the arrow Q1, it is necessary to make the arrangement relationship between the suction port 52 and the discharge port 53 opposite to the above.
- the outer rotor piece 221 is formed to have a uniform cross-sectional shape from the end portion on the X2 side to the end portion on the X1 side except for the notches 221f and 221g is shown.
- the present invention is not limited to this.
- the first engagement piece 221a and the second engagement piece 221b in the outer rotor piece 221 may be integrally connected in the radial direction at both ends along the X direction.
- the first engagement piece portion 221a, the second engagement piece portion 221b, and the side end portion connecting the first engagement piece portion 221a and the second engagement piece portion 221b at both ends in the X direction are circumferential.
- the outer rotor piece may be configured such that the engagement space 203 is formed in the concave portion surrounded by the inner space. Accordingly, the third engagement piece portion 221c is engaged with the engagement space 203 closed around the third engagement piece portion 221c.
- a communication hole that penetrates the second engagement piece 221b in the thickness direction may be provided instead of the notch 221f so that the engagement space 203 and the volume chamber 261 communicate with each other.
- the first engagement piece portion 221a and the second engagement piece portion 221b having a small thickness (thin) are integrally connected at both ends in the X direction. It is possible to improve the rigidity of the outer rotor piece that repeats the operation in which the third engagement piece 221c is projected and retracted.
- the oil pump 100 in which the discharge amount is variable according to the eccentric amount by translating the housing 40 with respect to the inner rotor 10 having the rotation center R fixed inside the pump body 50 is shown, the present invention is not limited to this.
- an oil pump with a constant discharge amount may be configured with a constant eccentric amount without translating the housing 40.
- the example in which the individual outer rotor pieces 21 (221) constituting the outer rotor 20 (220) are formed using an aluminum alloy has been described.
- the present invention is not limited to this. .
- the present invention is applied to the oil pump 100 (200, 300, 400) that supplies the oil (lubricating oil) 1 to the internal combustion engine (engine)
- the invention is not limited to this.
- the present invention may be applied to an oil pump for supplying AT fluid (AT oil) to an automatic transmission (AT) that automatically switches the gear ratio according to the rotational speed of the internal combustion engine.
- AT automatic transmission
- the lubricating oil is supplied to the sliding portion in the continuously variable transmission (CVT) capable of changing the gear ratio continuously and continuously.
- the present invention may be applied to an oil pump for this purpose.
- the present invention may be applied to an oil pump for supplying power steering oil to a power steering device that drives a steering (steering device) in a vehicle.
- the oil pump 100 (200, 300, 400) is mounted on a vehicle such as an automobile equipped with an internal combustion engine (engine)
- engine an internal combustion engine
- the present invention is not limited to this. I can't. For example, you may apply this invention with respect to the oil pump mounted in equipment other than the vehicle provided with the internal combustion engine (engine).
- an internal combustion engine a gasoline engine, a diesel engine, a gas engine, etc. are applicable.
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Abstract
Description
まず、図1~図7を参照して、本発明の第1実施形態によるオイルポンプ100の構成について説明する。なお、図1および図2では、オイルポンプ100を構成する主な構成要素に対して符号を付しており、図3~図7において、オイルポンプ100の詳細な構成(構造)に対して符号を付している。
次に、図2および図10~図14を参照して、第2実施形態について説明する。この第2実施形態では、上記第1実施形態において用いたアウタロータ20(図2参照)とは異なる形状を有するアウタロータ片221を組み合わせて環状のアウタロータ220を構成した例について説明する。なお、図10では、オイルポンプ200を構成する主な構成要素に対して符号を付しており、図11~図14において、オイルポンプ200の詳細な構成(構造)に対して符号を付している。また、図中において、上記第1実施形態と同様の構成には、第1実施形態と同じ符号を付して図示している。
まず、図1および図15~図23を参照して、本発明の第3実施形態によるオイルポンプ300の構成について説明する。なお、以下では、ポンプ要素35を収容するハウジング45の移動方向をY軸方向とし、これに対して直交するスプール部材360が移動する方向をZ軸方向とし、インナロータ10の回転軸方向をX軸方向として説明を行う。また、図中において、上記第1実施形態と同様の構成には、第1実施形態と同じ符号を付して図示している。なお、ハウジング45は、本発明の「ロータ収容部」の一例であり、スプール部材360は、本発明の「カム部材」の一例である。
次に、図15、図24および図25を参照して、第4実施形態について説明する。この第4実施形態では、上記第3実施形態において用いたスプール部材360(図15参照)とは異なるカム形状部462を有するスプール部材460を有してオイルポンプ400を構成した例について説明する。なお、図中において、上記第3実施形態と同様の構成には、第3実施形態と同じ符号を付して図示している。
5、8 係合空間(第1係合空間)
6、7 係合空間(第2係合空間)
10 インナロータ
12 ベーン収容部
12a 凹部(ベーン収容部)
20、220 アウタロータ
21、221 アウタロータ片
21a、221a 第1係合片部
21b、221b 第2係合片部
21c、221c 第3係合片部
21d 第4係合片部
21e、221e 基部(ベーン連結部)
21f、221f 切欠部(溝部)
21g、221g 切欠部(溝部)
21h、221h 係合部(ベーン連結部)
30 ベーン
31 基部(ベーン収容部に収容される部分)
32 先端部
35、235 ポンプ要素
40、45 ハウジング(ロータ収容部)
46 座部
47 凸部(カム係合部)
50、80 ポンプボディ
52 吸込ポート
53 吐出ポート
54 吐出油路
57 油路部
58a 受圧領域
58b 調整領域
61、261 容積室(第1容積変化部)
62、262 容積室(第2容積変化部)
63、263 容積室(第3容積変化部)
71 カム領域(第1カム領域)
72 カム領域(第2カム領域)
73、473 カム領域(第3カム領域)
74 カム領域
75、475 カム領域
81 ポンプ収容部
85 スプリング収納部
86 開口部
90 エンジン
100、200、300、400 オイルポンプ
201、202 係合空間(第1係合空間)
203 係合空間(第2係合空間)
305 スプリング(第1付勢部材)
306 スプリング(第2付勢部材)
360、460 スプール部材(カム部材)
361 本体部
362、462 カム形状部(カム領域)
363 座部
364 受圧面
365 連通孔
501、502 連通孔(穴部)
Claims (15)
- 複数のベーンが半径方向にスライド移動可能に収容されるベーン収容部を含むとともに、回転可能なインナロータと、
前記複数のベーンの半径方向外側の先端部が連結される複数のベーン連結部を含むとともに、回転可能な環状のアウタロータと、
前記インナロータと前記アウタロータとの間に設けられ、前記インナロータの前記アウタロータに対する偏心に応じて第1容積が変化することによりポンプ機能を有する第1容積変化部と、
前記アウタロータに設けられ、前記インナロータの前記アウタロータに対する偏心に応じて隣接する前記ベーン連結部間の周方向の距離が変化することにより、第2容積が変化することによってポンプ機能を有する第2容積変化部と、を備えた、オイルポンプ。 - 前記インナロータの前記アウタロータに対する偏心に応じて前記複数のベーンが半径方向にスライド移動することにより、前記インナロータの前記ベーン収容部における第3容積が変化することによってポンプ機能を有する第3容積変化部をさらに備える、請求項1に記載のオイルポンプ。
- オイルを吸い込む吸込ポートおよびオイルを吐出する吐出ポートをさらに備え、
前記吸込ポートでは、前記ベーン収容部に収容される前記ベーンが半径方向外側に徐々にスライド移動することにより、前記インナロータの前記ベーン収容部における前記第3容積が徐々に大きくなるとともに、前記吐出ポートでは、前記ベーン収容部に収容される前記ベーンが半径方向内側に徐々にスライド移動することにより、前記インナロータのベーン収容部における前記第3容積が徐々に小さくなるように構成されている、請求項2に記載のオイルポンプ。 - 前記ベーン収容部に収容される部分の前記ベーンの厚みは、一定である、請求項2または3に記載のオイルポンプ。
- 前記第2容積変化部は、前記インナロータの前記アウタロータに対する偏心に応じて前記ベーンの半径方向外側の先端部の半径方向のスライド位置が変化することにより、前記アウタロータにおける前記複数のベーン連結部間の周方向の距離が変化することによって、前記第2容積が変化可能に構成され、
前記アウタロータは、前記複数のベーン毎に設けられ、前記ベーン連結部を各々含む複数のアウタロータ片を含み、
前記複数のアウタロータ片は、隣接する前記アウタロータ片が互いの周方向の距離を変化可能に係合された状態で、円周状に配置され、
隣接する前記アウタロータ片は、前記第2容積変化部を構成する係合空間を有した状態で周方向に互いに係合するとともに、隣接する前記アウタロータ片間の周方向の距離が変化することにより、前記係合空間の前記第2容積が変化するように構成されている、請求項1~4のいずれか1項に記載のオイルポンプ。 - 前記第2容積変化部を構成する前記係合空間と前記第1容積変化部とを連通する溝または穴が設けられている、請求項5に記載のオイルポンプ。
- 前記第2容積変化部を構成する前記係合空間は、隣接する2つの前記ベーンのうち一方側に位置する第1係合空間と、前記隣接する2つの前記ベーンのうち他方側に位置する第2係合空間とを含む、請求項5または6に記載のオイルポンプ。
- オイルを吸い込む吸込ポートおよびオイルを吐出する吐出ポートをさらに備え、
前記アウタロータは、前記複数のベーン毎に設けられ、前記ベーン連結部を各々含む複数のアウタロータ片を含み、
前記吸込ポートでは、隣接する前記アウタロータ片間の周方向の距離が徐々に大きくなることにより前記第2容積が徐々に大きくなるとともに、前記吐出ポートでは、隣接する前記アウタロータ片間の周方向の距離が徐々に小さくなることにより前記第2容積が徐々に小さくなるように構成されている、請求項5~7のいずれか1項に記載のオイルポンプ。 - 前記インナロータを収容するとともに前記インナロータの偏心量を変化させるように第1方向に移動可能なロータ収容部と、
オイルを吸い込む吸込ポートおよびオイルを吐出する吐出ポートと、
前記吐出ポートからのオイルの吐出圧力に応じて前記第1方向と交差する第2方向に直線的に移動され、前記第2方向の一方方向への直線的な移動に伴って前記ロータ収容部を前記第1方向に移動させることによって前記インナロータの偏心量を増減させるように設けられたカム領域を含むカム部材と、をさらに備えた、請求項1~8のいずれか1項に記載のオイルポンプ。 - 前記カム部材は、オイルの吐出圧力に応じて前記第2方向に直線的に移動されるスプール部材を含み、
前記ロータ収容部は、前記スプール部材の前記カム領域に対向するように配置されたカム係合部を含み、
前記スプール部材の前記カム領域は、前記ロータ収容部の前記カム係合部に対する突出量が前記第2方向に沿って変化されるとともに、前記スプール部材の前記第2方向の一方方向への移動に伴う前記カム領域の突出量の変化に応じて前記ロータ収容部が前記第1方向に移動されて前記インナロータの偏心量が増減されるように構成されている、請求項9に記載のオイルポンプ。 - 前記スプール部材の前記カム領域は、
前記吐出ポートからのオイルの吐出圧力が第1圧力範囲にある場合に、前記ロータ収容部の前記カム係合部に対向配置される第1カム領域と、
前記吐出ポートからのオイルの吐出圧力が前記第1圧力範囲よりも大きい第2圧力範囲にある場合に、前記ロータ収容部の前記カム係合部に係合する第2カム領域と、
前記吐出ポートからのオイルの吐出圧力が前記第2圧力範囲よりも大きい第3圧力範囲にある場合に、前記ロータ収容部の前記カム係合部に係合する第3カム領域と、を含み、
前記吐出ポートからのオイルの吐出圧力の増加に応じて、前記第1カム領域、前記第2カム領域および前記第3カム領域へと前記カム部材の前記カム領域が順次切り替わるように前記スプール部材が前記第2方向の一方方向に移動された場合に、
前記第2カム領域において前記インナロータの回転中心に対する前記ロータ収容部の前記第1方向の移動量および前記インナロータの偏心量が減少されるとともに、前記第2カム領域において前記インナロータの回転中心に対する前記ロータ収容部の前記第1方向の移動量および前記インナロータの偏心量が減少された状態から、前記第3カム領域において前記ロータ収容部の前記第1方向の移動量および前記インナロータの偏心量が増加されるように構成されている、請求項10に記載のオイルポンプ。 - 前記第1カム領域は、前記ロータ収容部の前記第1方向への移動に伴う前記インナロータの偏心量が第1偏心量になるように形成され、
前記第2カム領域は、前記ロータ収容部の前記第1方向への移動に伴う前記インナロータの偏心量が前記第1偏心量よりも小さい第2偏心量になるように形成され、
前記第3カム領域は、前記ロータ収容部の前記第1方向への移動に伴う前記インナロータの偏心量が前記第2偏心量の最小値よりも大きい第3偏心量になるように形成されている、請求項11に記載のオイルポンプ。 - 前記第2カム領域は、前記第3カム領域に向かって前記インナロータの偏心量が前記第1偏心量から前記第2偏心量に減少するように設けられており、
前記第3カム領域は、前記第2カム領域とは反対側に向かって前記インナロータの偏心量が前記第2偏心量から前記第3偏心量に増加するように設けられている、請求項12に記載のオイルポンプ。 - 前記第1圧力範囲において、前記スプール部材の前記第1カム領域が前記ロータ収容部の前記カム係合部に対応する位置に直線的に移動されることにより、前記ロータ収容部が前記第1方向の第1偏心位置に直線的に移動されて、最大の偏心量である第1偏心量になるように構成され、
前記第2圧力範囲において、前記スプール部材の前記第2カム領域が前記ロータ収容部の前記カム係合部に係合する位置に直線的に移動されることにより、前記ロータ収容部が前記第1方向の第2偏心位置に直線的に移動されて、前記第1偏心量よりも小さい第2偏心量になるように構成され、
前記第3圧力範囲において、前記スプール部材の前記第3カム領域が前記ロータ収容部のカム係合部に係合する位置に直線的に移動されることにより、前記ロータ収容部が前記第1方向の第3偏心位置に直線的に移動されて、前記第2偏心量の最小値よりも大きい第3偏心量になるように構成されている、請求項11~13のいずれか1項に記載のオイルポンプ。 - 前記ロータ収容部を前記カム部材側に付勢する第1付勢部材と、
前記カム部材を前記吐出ポート側の位置に向かうように付勢する第2付勢部材をさらに備える、請求項9~14のいずれか1項に記載のオイルポンプ。
Priority Applications (3)
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US14/916,901 US10030655B2 (en) | 2013-09-24 | 2014-09-01 | Oil pump |
EP14849424.8A EP3051134B1 (en) | 2013-09-24 | 2014-09-01 | Oil pump |
CN201480052617.6A CN105579706B (zh) | 2013-09-24 | 2014-09-01 | 油泵 |
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JP2013196376A JP6123606B2 (ja) | 2013-09-24 | 2013-09-24 | オイルポンプ |
JP2013-196376 | 2013-09-24 | ||
JP2013224862A JP6171852B2 (ja) | 2013-10-30 | 2013-10-30 | オイルポンプ装置 |
JP2013-224862 | 2013-10-30 |
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WO2015045744A1 true WO2015045744A1 (ja) | 2015-04-02 |
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Cited By (2)
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WO2016076020A1 (ja) * | 2014-11-12 | 2016-05-19 | アイシン精機株式会社 | オイルポンプ |
CN114484251A (zh) * | 2022-02-14 | 2022-05-13 | 浙江机电职业技术学院 | 一种滑块式机油泵 |
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JP2018096268A (ja) * | 2016-12-13 | 2018-06-21 | 株式会社マーレ フィルターシステムズ | ポンプ |
DE102017210776A1 (de) * | 2017-06-27 | 2018-12-27 | Mahle International Gmbh | Pendelschieberzellenpumpe |
JP6885812B2 (ja) * | 2017-07-12 | 2021-06-16 | 株式会社山田製作所 | 油圧制御装置及び油圧制御方法 |
KR102406147B1 (ko) * | 2017-12-05 | 2022-06-07 | 현대자동차 주식회사 | 가변 오일펌프의 제어시스템 |
CN113994095A (zh) | 2019-05-23 | 2022-01-28 | 皮尔伯格泵技术有限责任公司 | 可变排量润滑剂泵 |
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Also Published As
Publication number | Publication date |
---|---|
US20160215775A1 (en) | 2016-07-28 |
CN105579706A (zh) | 2016-05-11 |
US10030655B2 (en) | 2018-07-24 |
CN105579706B (zh) | 2018-02-09 |
EP3051134A1 (en) | 2016-08-03 |
EP3051134A4 (en) | 2016-08-24 |
EP3051134B1 (en) | 2018-05-30 |
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