US20150226212A1 - Rotating pump - Google Patents
Rotating pump Download PDFInfo
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- US20150226212A1 US20150226212A1 US14/614,805 US201514614805A US2015226212A1 US 20150226212 A1 US20150226212 A1 US 20150226212A1 US 201514614805 A US201514614805 A US 201514614805A US 2015226212 A1 US2015226212 A1 US 2015226212A1
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- United States
- Prior art keywords
- pressure
- rotor
- low
- pressure region
- deformation
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C19/00—Sealing arrangements in rotary-piston machines or engines
- F01C19/005—Structure and composition of sealing elements such as sealing strips, sealing rings and the like; Coating of these elements
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
- F04C2/14—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
- F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
- F04C15/0007—Radial sealings for working fluid
- F04C15/0015—Radial sealings for working fluid of resilient material
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
- F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
- F04C15/0034—Sealing arrangements in rotary-piston machines or pumps for other than the working fluid, i.e. the sealing arrangements are not between working chambers of the machine
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- 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
- F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
- F04C2/102—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member the two members rotating simultaneously around their respective axes
Definitions
- This disclosure relates generally to a rotating pump designed to suck and then discharge fluid, and more particularly to such a rotating pump which is useful for a brake system working to suck and discharge brake fluid to regulate the pressure thereof for controlling the braking force.
- Japanese Patent First Publication No. 2002-295376 teaches use of an internal gear pump, such as a trochoid pump, as a rotating pump for an automotive brake system.
- This type of rotating pump is made up of an inner rotor, an outer rotor, and a casing.
- the inner rotor is equipped with outer teeth formed on an outer periphery thereof.
- the outer rotor is equipped with inner teeth formed on an inner periphery thereof.
- the outer and inner rotors are mounted in the casing. Specifically, within the casing, the teeth of the inner rotor mesh with those of the outer rotor to define a plurality of cavities (i.e., clearances).
- the pump has an inlet port (i.e., a suction side) and an outlet port (i.e., a discharge side) which are diametrically opposed to each other across the center line of the pump.
- the inner rotor In operation of the pump, the inner rotor is rotated by a drive shaft, so that the outer rotor is rotated in the same direction as the inner rotor through the meshing of the outer teeth and the inner teeth. This causes the volumes of the cavities to increase and then decrease continuously to suck fluid from the inlet port and then discharge it from the outlet port every 360° rotation of the outer and inner rotors.
- the casing has two cavities formed on portions of the inner circumference thereof which face the outer circumference of the outer rotor. Sealing mechanisms each made up of a resin member and a rubber member are disposed in the cavities, respectively. The rubber member is placed on the bottom of the cavity of the casing, while the resin member is laid between the rubber member and the outer rotor. The rubber member, thus, presses the resin member into constant abutment with the peripheral surface of the outer rotor to hermetically seal between the low-pressure region and the high-pressure region.
- a rotating pump which may be employed in a brake system for automotive vehicles.
- the rotating pump comprises: (a) a drive shaft; (b) a rotor assembly made up of an outer rotor and an inner rotor, the outer rotor having inner teeth formed on an inner periphery thereof, the inner rotor having outer teeth formed on an outer periphery thereof and being rotated by the drive shaft around an axis defined by the drive shaft, the outer teeth meshing with the inner teeth of the outer rotor to define a plurality of cavities; (c) a casing in which the drive shaft is installed, the casing including a rotor chamber in which the rotor assembly is mounted to be rotatable with a gap formed between an inner peripheral surface of the casing which faces the outer rotor and an outer peripheral surface of the outer rotor, the casing having an inlet port from which fluid is sucked into the rotor assembly and an outlet port from which the fluid is discharged with rotation of the rotor
- Each of the first and second sealing members is made up of a seal functioning portion and an elastically pressing portion.
- the seal functioning portion is placed in contact with the outer periphery of the outer rotor and a low-pressure side surface that is a portion of an inner wall surface of a corresponding one of the first and second recesses which is closer to the low-pressure region than to the high-pressure region to establish a difference in pressure between the low-pressure region and the high-pressure region.
- the elastically pressing portion is located closer to a bottom of a corresponding one of the first and second recesses than the seal functioning portion is and works to press the seal functioning portion against the outer periphery of the outer rotor.
- the seal functioning portion includes a resinous member and a deformation-suppressing member.
- the resinous member is placed in contact with the outer periphery of the outer rotor and the low-pressure side surface of the inner wall surface of a corresponding one of the first and second recesses to establish the difference in pressure between the low-pressure region and the high-pressure region.
- the deformation-suppressing member is made of material which is more rigid than that of the resinous member and located closer to the low-pressure region than the resinous member is. A boundary between a surface of the deformation-suppressing member which faces the low-pressure side surface and a surface of the resinous member which faces the low-pressure side surface is located inside a corresponding one of the recesses.
- the first and second sealing members are, as described above, installed in the casing to hermetically isolate between the low-pressure region and the high-pressure region in the gap. Specifically, the seal functioning portion of each of the first and second sealing members is pressed by an elastically reactive force, as produced by the elastically pressing portion, and the high pressure of the fluid in the gap toward the low-pressure region in the gap, thereby bringing the resinous member into constant abutment with the inner wall of a corresponding of the first and second recesses in addition to the outer periphery of the outer rotor and an inner wall of the casing to establish a hermetic seal between the high-pressure region and the low-pressure region in the gap.
- the resinous member is pressed by the high pressure of the fluid, but stopped by the deformation-suppressing member of the seal functioning portion from being deformed into the low-pressure region of the gap, thereby minimizing the risk of breakage of the resinous member to ensure the stability of sealing the gap. This enables the rotating pump to discharge the fluid at an increased pressure.
- FIG. 1 is a circuit diagram which illustrates a brake system equipped with a rotating pump according to the first embodiment of the invention
- FIG. 2 is a partially sectional view which illustrates an internal structure of the rotating pump of FIG. 1 ;
- FIG. 3( a ) is an enlarged view of a sealing member shown in FIG. 2 ;
- FIG. 3( b ) is an illustration which shows a seal functioning portion of a sealing member, as viewed in an axial direction of a drive shaft of the rotating pump of FIG. 2 ;
- FIG. 3( c ) is an illustration of the seal functioning portion of FIG. 3( b ), as viewed from the center of the rotating pump in a radius direction of the drive shaft;
- FIG. 4 is an illustration which shows layout of the sealing member shown in FIG. 2 , as viewed from the center of the rotating pump in a radius direction of a drive shaft of the rotating pump;
- FIG. 5 is an illustration which shows a first modification of a sealing member, as viewed in an axial direction of a drive shaft of the rotating pump of FIG. 2 ;
- FIG. 6 is an illustration which shows a second modification of a sealing member, as viewed in an axial direction of a drive shaft of the rotating pump of FIG. 2 ;
- FIG. 7 is an illustration which shows a third modification of a sealing member, as viewed in an axial direction of a drive shaft of the rotating pump of FIG. 2 ;
- FIG. 8( a ) is an illustration which shows a first modification of a joining structure of a resinous member and a deformation-suppressing member of a sealing member, as viewed in an axial direction of a drive shaft of the rotating pump of FIG. 2 ;
- FIG. 8( b ) is a sectional illustration of the joining structure in FIG. 8( a ), as viewed from the center of the rotating pump in a radius direction of the drive shaft;
- FIG. 9( a ) is an illustration which shows a second modification of a joining structure of a resinous member and a deformation-suppressing member of a sealing member, as viewed in an axial direction of a drive shaft of the rotating pump of FIG. 2 ;
- FIG. 9( b ) is a sectional illustration of the joining structure in FIG. 9( a ), as viewed in a radius direction of the drive shaft;
- FIG. 10( a ) is an illustration which shows a third modification of a joining structure of a resinous member and a deformation-suppressing member of a sealing member, as viewed in an axial direction of a drive shaft of the rotating pump of FIG. 2 ;
- FIG. 10( b ) is a sectional illustration of the joining structure in FIG. 10( a ), as viewed in a radius direction of the drive shaft;
- FIG. 11 is an illustration which shows a fourth modification of a joining structure of a resinous member and a deformation-suppressing member of a sealing member, as viewed in an axial direction of a drive shaft of the rotating pump of FIG. 2 .
- FIG. 1 there is shown an automotive brake system equipped with a rotating pump that is a part of a hydraulic circuit of the brake system.
- the brake system as referred to herein, is designed as a so-called diagonal split system which includes two brake hydraulic circuits one of which controls the right front and the left rear wheel and the other of which controls the left front and the right rear wheel, but may be engineered as a front/rear split system.
- the brake system is equipped with a brake pedal 1 (i.e., a brake actuating member) to be depressed by a vehicle occupant or driver for applying the brakes to the vehicle, a brake booster 12 , a master cylinder 3 , wheel cylinders 4 and 5 , and a brake pressure control actuator 6 .
- the master cylinder 3 works to produce a braking hydraulic pressure in response to an operation of the brake actuating member (i.e., the brake pedal 1 ).
- the brake pedal 1 is connected to the brake booster 2 and the master cylinder 3 .
- the brake booster 2 works to boost the pressure applied to the brake pedal 1 .
- the brake booster 2 is equipped with a push rod which works to push master pistons installed in the master cylinder 3 , thereby developing the pressure (which will also be referred to as M/C pressure below).
- a master reservoir 3 a is connected which stores therein an excess of the brake fluid in the master cylinder 3 .
- the M/C pressure is transmitted to the front right wheel cylinder 4 and the rear left wheel cylinder 5 as wheel cylinder (W/C) pressure.
- the brake pressure control actuator 6 is disposed between the master cylinder 3 and the wheel cylinders 4 and 5 and works to control the W/C pressure, as developed in each of the wheel cylinders 4 and 5 .
- the brake pressure control actuator 6 includes a first hydraulic circuit and a second hydraulic circuit.
- the first hydraulic circuit is a hydraulic circuit working to control the brake fluid to be applied to the front right wheel FR (i.e., the wheel cylinder 4 ) and the left rear wheel RL (i.e., the wheel cylinder 5 ).
- the second hydraulic circuit is a hydraulic circuit working to control the brake fluid to be applied to the left front wheel FL and the right rear wheel RR.
- the first hydraulic circuit and the second hydraulic circuit are substantially identical in structure with each other. The following discussion will refer only to the first hydraulic circuit for the brevity of disclosure.
- the brake system (i.e., the first hydraulic circuit) is equipped with a main hydraulic line A (also called a main hydraulic path below) connecting with the master cylinder 3 .
- the main hydraulic line A has disposed therein a differential pressure control valve 7 which divides the main hydraulic line A into two: a pipe line A 1 which is a hydraulic line extending from the master cylinder 3 to the differential pressure control valve 7 and subjected to the M/C pressure and a pipe line A 2 which is a hydraulic line extending from the differential pressure control valve 7 to the wheel cylinders 4 and 5 .
- the differential pressure control valve 7 is operable in either of two modes: an open mode and a pressure-difference mode. In a normal braking mode where it is required to produce the braking force as a function of an amount of depression of the brake pedal 11 by the driver, the valve position of the differential pressure control valve 7 is placed in the open mode. When the valve position of the differential pressure control valve 7 is placed in the pressure-difference mode, the differential pressure control valve 7 works to control the flow of the braking fluid to elevate and hold the W/C pressures above the M/C pressure by a pressure difference, as developed by the differential pressure control valve 7 .
- the pipe line A 2 includes two branch lines: one being equipped with a pressure-increasing valve 8 a which increases the pressure of the brake fluid supplied to the wheel cylinder 4 , and one being equipped with a pressure-increasing valve 8 b which increases the pressure of the brake fluid supplied to the wheel cylinder 5 .
- Each of the pressure-increasing valves 8 a and 8 b is implemented by a two-position valve which is opened or closed by a brake electronic control unit (ECU), not shown, to control increasing of the braking hydraulic pressure (i.e., the pressure of the brake fluid applied to the wheel cylinder 4 or 5 ).
- ECU brake electronic control unit
- the pressure-increasing valve 8 a is opened, the pressure of the brake fluid, as created by the M/C pressure, is transmitted to the wheel cylinder 4 .
- brake fluid pressure control such as an anti-lock brake control, is not executed, the pressure-increasing valve 8 a is opened.
- the pressure-increasing valve 8 b is implemented by a two-position valve which is opened or closed by a brake electronic control unit (ECU), not shown, to control increasing of the braking hydraulic pressure (i.e., the pressure of the brake fluid applied to the wheel cylinder 4 or 5 ).
- the pressure-increasing valve 8 a is opened
- the brake pressure control actuator 6 also includes a hydraulic line B which extends as a pressure-reducing path between a pressure control reservoir 9 and a junction of the pressure-increasing valve 8 a and the wheel cylinder 4 and between the pressure control reservoir 9 and a junction of the pressure-increasing valve 8 b and the wheel cylinder 5 .
- the brake fluid is drained to the pressure control reservoir 9 through the hydraulic line B to control the W/C pressure exerted on the wheel cylinders 4 and 5 to prevent the wheels of the vehicle from locking.
- the hydraulic line B is equipped with pressure-reducing valves 10 a and 10 b which are each implemented by a two-position solenoid valve.
- the pressure-reducing valves 10 a and 10 b are opened or closed by the brake ECU to control decreasing of the braking hydraulic pressure (i.e., the pressure of the brake fluid applied to the wheel cylinder 4 or 5 ).
- the pressure-reducing valves 10 a and 10 b are kept closed.
- the pressure-reducing valves 10 a and 10 b are opened.
- the brake pressure control actuator 6 also includes a hydraulic line C which extends between the pressure control reservoir 9 and the hydraulic line A.
- the hydraulic line C is equipped with a pump 11 which is disposed between a junction of the differential pressure control valve 7 and the pressure-increasing valves 8 a and 8 b and driven by an electric motor 12 .
- the hydraulic line C also has check valves 11 a and 11 b mounted across the pump 11 .
- the hydraulic line C is also equipped with an accumulator 13 disposed downstream of the pump 11 to alleviate pulsation of the brake fluid discharged from the pump 11 .
- the brake pressure control actuator 6 also includes a hydraulic line D which extends as a sub-hydraulic line between the pressure control reservoir 9 and the master cylinder 3 .
- the pump 11 works to suck the brake fluid from the hydraulic line A 1 through the hydraulic line D and the pressure control reservoir 9 and output it to the hydraulic line A 2 to elevate the W/C pressures.
- the second hydraulic circuit has the same structure as described above as that of the first hydraulic circuit.
- the control valves 7 , 8 a , 8 b , 10 a , and 10 b , the rotating pump 11 , the pressure control reservoir 9 , and the motor 12 are installed in a housing which is drilled to define the above described hydraulic lines and constitute the brake pressure control actuator 6 .
- the brake pressure control actuator 6 is, as described above, disposed between the master cylinder 3 and the wheel cylinders 4 and 4 , thereby making the brake system, as illustrated in FIG. 1 .
- the brake system works to execute brake fluid pressure control tasks such as the ABS control, the brake assist control, the adaptive cruise control, and the regenerative braking control and drive the rotating pump 11 to suck or discharge the brake fluid.
- brake fluid pressure control tasks such as the ABS control, the brake assist control, the adaptive cruise control, and the regenerative braking control and drive the rotating pump 11 to suck or discharge the brake fluid.
- it has been required to develop the high W/C pressure quickly; for example, in the brake assist control mode or the adaptive cruise control mode where it is necessary to actuate the rotating pump 11 to create a high pressure of brake fluid.
- the discharge pressure of the rotating pump 11 is, thus, required to be increased.
- the rotating pump 11 of this embodiment is engineered in the following way.
- the structure of the rotating pump 11 will be described in detail with reference to FIGS. 2 , 3 , and 4 .
- the rotating pump 11 is installed in a rotor chamber 50 a of a casing 50 .
- an outer rotor 51 and an inner rotor 52 are arranged with center axes X and Y thereof being eccentric from each other.
- a combination of the outer rotor 51 and the inner rotor 52 works as a rotor assembly in the rotating pump 11 .
- the outer rotor 51 has inner teeth 51 a formed on an inner periphery thereof.
- the inner rotor 52 has outer teeth 52 a formed on an outer periphery thereof.
- the inner teeth 51 a of the outer rotor 51 mesh with the outer teeth 52 a of the inner rotor 52 so as to create a plurality of gaps or enclosed cavities 53 therebetween. More specifically, surfaces of the inner teeth 51 a and the outer teeth 52 a are placed in contact with each other to define the cavities 53 .
- the outer rotor 51 and the inner rotor 52 are rotated by a drive shaft 54 arranged in the center of the inner rotor 52 , so that the cavities 53 are changed in volume thereof with rotation of the drive shaft 54 , thereby sucking or discharging the brake fluid.
- the thus constructed rotating pump 11 is a multi-tooth trochoid pump with no crescent in which the inner teeth 51 a of the outer rotor 51 and the outer teeth 52 a of the inner rotor 52 mesh with each other to define the cavities 53 .
- the meshing surfaces of the outer teeth 52 a contact at a plurality of points with those of the inner teeth 51 a to transmit torque from the inner rotor 52 to the outer rotor 51 .
- the casing 50 includes a center plate 50 b and side plates 50 c and 50 d , as illustrated in FIG. 4 .
- the center plate 50 b embraces the outer peripheries of the rotors 51 and 52 .
- the side plates 50 c and 50 d sandwich axially-opposed end surfaces of the rotors 51 and 52 and the center plate 50 b .
- the center plate 50 b and the side plates 50 c and 50 d form a space which defines the rotor chamber 50 a .
- the side plates 50 c and 50 d have center holes (not shown) in which the drive shaft 54 is fit.
- the outer rotor 51 and the inner rotor 52 are disposed to be rotatable within the rotor chamber 50 a .
- a rotatable assembly of the outer rotor 51 and the inner rotor 52 is arranged rotatably in the rotor chamber 50 a of the casing 50 , so that the outer rotor 51 may rotate about the axis X, and the inner rotor 52 may rotate about the axis Y.
- the axis Y is an axis of rotation of the inner rotor 52 defined by the drive shaft 54 (i.e., a longitudinal center line of the drive shaft 54 ).
- the side plate 50 c has an inlet port 60 and an outlet port 61 which are located on the left and right sides of the center line Z and communicate with the rotor chamber 50 a .
- the inlet port 60 communicates with some of the cavities 53 through which the brake fluid is sucked into the pump 11 .
- the outlet port 61 which communicates with some of the cavities 53 through which the brake fluid is discharged from the pump 11 .
- the enclosed cavity 53 a that is one of the cavities 53 which has the greatest volume does not communicate with the inlet port 60 or with the outlet port 61 .
- the cavity 53 a works to develop a difference between the suction pressure in the inlet port 60 and the discharge pressure in the outlet port 61 .
- One of the side plates 50 c and 50 d has a first flow path and a second flow path formed therein.
- the first flow path communicates between an annular gap S on the outer circumference of the outer rotor 51 , that is, a clearance between the outer periphery of the outer rotor 51 and the inner wall of the casing 50 (i.e., the inner wall of the rotor chamber 50 a ) and the inlet port 60 , while the second flow path communicates between the gap S and the outlet port 61 .
- the gap S is, as can be seen in FIG. 2 , blocked on the side of the outlet port 61 .
- the center plate 50 b of the casing 50 has recesses 50 e and 50 f formed in the inner wall thereof.
- the recesses 50 e and 50 f will also be referred to as a first and a second recess below.
- Each of the recesses 50 e and 50 f is located at a given angle away from the center line Z toward the inlet port 60 around the axis Y (i.e., the rotating center) of the outer rotor 51 .
- each of the recesses 50 e and 50 f lies on a circle, as defined about the axis Y, and is separate from the center line Z by the given angle.
- Sealing members 80 and 90 are mounted in the recesses 50 e and 50 f to stop the brake fluid from flowing within the gap S on the outer circumference of the outer rotor 51 .
- the sealing members 80 and 90 are separate from each other in a circumferential direction of the outer rotor 51 through a portion of the gap S which faces and communicates with the inlet port 60 .
- the sealing members 80 and 90 will also be referred to as a first and a second sealing member below.
- the sealing members 80 and 90 work to hermetically isolate a high-pressure portion (i.e., the high-pressure region) and a low-pressure portion (i.e., the low-pressure region) of the gap S, thereby avoiding the flow of the brake fluid from the high-pressure region to the low-pressure region.
- the sealing members 80 and 90 serve to keep a portion of the gap S which communicates with the inlet port 60 at the suction pressure and a portion of the gap S which communicates with the outlet port 61 at the discharge pressure, thereby developing a balance in pressure between outside and inside the outer rotor 51 .
- FIGS. 3( a ) to 3 ( c ) illustrate the structure of the sealing member 80 in detail.
- the sealing member 90 is identical in structure with the sealing member 80 .
- the following discussion will, thus, refer only to the sealing member 80 for the sake of simplicity of explanation.
- the sealing member 80 is, as can be seen in FIGS. 3( a ) to 3 ( c ), made up of two parts: a seal functioning portion 81 and an elastically pressing portion 82 .
- the seal functioning portion 81 is pressed against the circumferential surface of the outer rotor 51 and the side plates 50 c and 50 d to establish a hermetical seal in the gap S, that is, to seal between the high-pressure region and the low-pressure region.
- the seal functioning portion 81 is made up of a resinous block 81 a and a deformation-suppressing block 8 b .
- the seal functioning portion 81 is substantially of a pentagonal prism shape.
- the main part of the seal functioning portion 81 is made of the resinous block 81 a , while the other part of the seal functioning portion 81 is made of the deformation-suppressing block 81 b to define a surface of the seal functioning portion 81 exposed to the low-pressure region of the gap S.
- the deformation-suppressing block 81 b is arranged so as to define a portion of the seal functioning portion 81 which is exposed to the low-pressure region of the gap S, while the resinous block 81 a is shaped or located so as not to be exposed to the low-pressure region of the gap S.
- the resinous block 81 a is made of a soft resin such as Teflon (Trade Mark).
- the resinous block 81 a is shaped to have outer surfaces contacting the outer circumference of the outer rotor 51 (see FIG. 3( a )), the side plates 50 c and 50 d (see FIG. 4) , and the inner wall surface of the recess 50 e , i.e., a portion (which will also be referred to as a low-pressure side surface below) of the inner wall of the recess 50 e which is closer to the low-pressure side than to the high-pressure side in the gap S.
- the circumference (i.e., the outer peripheral surface) and the side surfaces of the deformation-suppressing block 81 b are substantially entirely enclosed or surrounded by the surfaces of the recess 50 e , the resinous block 81 a , the side plates 50 c and 50 d , and the outer rotor 51 , thereby hermetically isolating between the high-pressure region and the low-pressure region in the gap S to develop a desired difference in pressure between the high-pressure region and the low-pressure region.
- the resinous block 81 a is shaped to have a dimension (i.e., length L 1 in FIG.
- the resinous block 81 a is also shaped to have the flat surface 81 aa , as illustrated in FIGS. 3( a ) and 3 ( b ), which is diagonally opposed to the surface thereof with which the deformation-suppressing block 81 b is placed in contact.
- the surface 81 aa may be formed to extend substantially parallel to the surface the deformation-suppressing block 81 b contacts.
- the elastically pressing portion 82 of the sealing member 80 is urged into abutment with the surface 81 aa of the resinous block 81 a .
- the deformation-suppressing block 81 b is made from material such as resin or metal which is more rigid than the resinous block 81 a and works as a stopper to stop the resinous block 81 a from elastically deforming toward the gap S. Specifically, the deformation-suppressing block 81 b is located to be exposed to the low-pressure region of the gap S. In other words, the deformation-suppressing block 81 b lies at a portion of the seal functioning portion 81 which is exposed to the low-pressure region of the gap S, so that the resinous block 81 a is not exposed to the low-pressure region.
- the deformation-suppressing block 81 b is formed in the shape of a triangular prism made of two triangular bases and three side faces where the triangular bases are the end surfaces of the deformation-suppressing block 81 b which face the side plates 50 c and 50 d , and the side faces are the side surfaces of the deformation-suppressing block 81 b which extend in the axial direction of the outer rotor 51 .
- the deformation-suppressing block 81 b is dimensionally formed so that one of the side surfaces thereof partially faces or is partially exposed to the gap S, and a boundary 100 , as illustrated in FIG.
- the deformation-suppressing block 81 b is also shaped to have a dimension (i.e., length L 2 ) in the same direction as the axial direction of the outer rotor 51 (i.e., a direction parallel to the axis of rotation of the inner rotor 52 ) which is, as can be seen from FIG. 4 , set smaller than the thickness of the rotor chamber 50 a in the axial direction of the outer rotor 51 (i.e., the minimum interval between the side surfaces of the side plates 50 c and 50 d ).
- the resinous block 81 a and the deformation-suppressing block 81 b may be mechanically joined together or separate from each other. In this embodiment, they are joined together.
- the resinous block 81 a as illustrated in FIG. 3( c ), has a wedge-shaped recess 81 ab formed in the surface thereof which diagonally faces the outer rotor 51 .
- the wedge-shaped recess 81 ab is shaped to have a depth, as can be seen from FIG. 3( b ), substantially extending from the side of the low-pressure region to the side of the high-pressure region of the gap S.
- the wedge-shaped recess 81 ab is recessed from the side of the low-pressure region to the side of the high-pressure region of the gap S.
- the deformation-suppressing block 81 b is shaped to have a wedge-shaped protrusion 81 ba formed on the surface thereof which faces the resinous block 81 a .
- the wedge-shaped protrusion 81 ba projects toward the high-pressure region of the gap S.
- the wedge-shaped protrusion 81 ba is fit in the wedge-shaped recess 81 ab to establish the joint of the resinous block 81 a and the deformation-suppressing block 81 b.
- the seal functioning portion 81 is made up of the resinous block 81 a and the deformation-suppressing block 81 b in the above way.
- the elastically pressing portion 82 is made of an elastically deformable material such as rubber and located deeper than the seal functioning portion 81 within the recess 50 e , in other words, closer to the bottom of the recess 50 e than the seal functioning portion 81 is.
- the elastically pressing portion 82 is elastically deformed within the recess 50 e , thereby creating a reactive force which presses the resinous block 81 a of the seal functioning portion 81 against the outer wall surface of the outer rotor 51 and the inner wall surface of the recess 50 e .
- the elastically pressing portion 82 is elastically deformed between the inner wall surface of the recess 50 e and the surface 81 aa of the resinous block 81 a of the seal functioning portion 81 , thereby pressing the surface 81 a a to urge the resinous block 81 a against the inner wall of the recess 50 e and the outer circumference of the outer rotor 51 .
- This establishes a liquid-tight seal in the gap S, that is, hermetically blocks the gap S to isolate between the high-pressure region and the low-pressure region.
- the control valves 7 and 30 to 33 are actuated according to the control mode, as specified by the one of the brake fluid pressure control tasks. Simultaneously, the motor 12 is actuated to suck and then discharge the brake fluid through the pump 11 .
- the inner rotor 51 of the pump 11 is rotated by the drive shaft 54 , thereby rotating the outer rotor 51 in the same direction as the inner rotor 51 through the meshing of the inner teeth 51 a with the outer teeth 52 a .
- the volumes of the cavities 53 are changed sequentially every rotation of the outer rotor 51 and the inner rotor 52 , thereby sucking the brake fluid from the inlet port 60 and then discharge it from the outlet port 61 to the hydraulic line A 2 to elevate the W/C pressure.
- the rotating pump 11 performs a normal pumping operation in which the rotors 51 and 52 are rotated to suck the brake fluid from the inlet port 60 and then discharge it from the outlet port 61 .
- a portion of the gap S on the outer circumference of the outer rotor 51 communicating with the inlet port 60 is kept at the suction pressure, while a portion of the gap S communicating with the outlet port 61 is kept at the discharge pressure. This creates, as described above, the low-pressure region and the high-pressure region in the gap S.
- the sealing members 80 and 90 are, as described above, installed in the center plate 50 b of the casing 50 to hermetically isolate between the low-pressure region and the high-pressure region in the gap S. Specifically, the seal functioning portion 81 of each of the sealing members 80 and 90 is pressed by the elastically reactive force, as produced by the elastically pressing portion 82 , and the high pressure of the brake fluid in the gap S toward the low-pressure region in the gap S, thereby bringing the resinous block 81 a into constant abutment with the inner wall of the recess 50 e in addition to the outer circumferential surface of the outer rotor 51 and the surfaces of the side plates 50 c and 50 d to establish the hermetic seal between the high-pressure region and the low-pressure region in the gap S.
- the resinous block 81 a is pressed by the high pressure of the brake fluid, but stopped by the deformation-suppressing block 81 b of the seal functioning portion 81 from being deformed into the low-pressure region of the gap S, thereby minimizing the risk of breakage of the resinous block 81 a to ensure the stability of sealing the gap S. This enables the rotating pump 11 to discharge the brake fluid at an increased pressure.
- the seal functioning portion 81 of each of the sealing members 80 and 90 may be engineered to have the resinous block 81 a and the deformation-suppressing block 81 b which are mechanically separate from each other.
- the deformation-suppressing block 81 b may be, as illustrated in FIG. 6 , formed in the shape of a circular cylinder made of two circular bases and a side face substantially perpendicular to the circular bases where the circular bases are the end surfaces of the deformation-suppressing block 81 b which face the side plates 50 c and 50 d , and the side face is the side surface of the deformation-suppressing block 81 b which extends in the axial direction of the outer rotor 51 .
- the resinous block 81 a when the rotating pump 11 is at rest in operation, the resinous block 81 a is located far away from the deformation-suppressing block 81 b on a portion of the inner surface of, for example, the recess 50 e which is closer to the low-pressure region than to the high-pressure region of the gap S, thus facilitating the ease of elastic deformation of the resinous block 81 a into the gap S.
- This problem may be alleviated by making the deformation-suppressing block 81 b to have a radius greater than the thickness of the gap S (i.e., the dimension of the gap S in the radius direction of the outer rotor 50 ).
- the deformation-suppressing block 81 b be shaped so that a boundary between the resinous block 81 a and the deformation-suppressing block 81 b on a portion of the inner wall of, for example, the recess 50 e which is closer to the low-pressure region than to the high-pressure region fully lies, like in the first embodiment, inside the recess 50 e when the resinous block 81 a is deformed most greatly.
- the deformation-suppressing block 81 b is of a shape other than the triangular prism or the circular cylinder.
- the deformation of the resinous block 81 a into the gap S is avoided by making the deformation-suppressing block 81 b to have a dimension greater than that of the gap S in the radius direction of the drive shaft 54 (i.e., the outer rotor 51 ) so that the deformation-suppressing block 81 b is at least partially placed in contact with the inner wall of the recess 50 e.
- the deformation-suppressing block 81 b may alternatively be, as illustrated in FIG. 7 , formed in the shape of a quadrangular prism made of two square or rectangular bases and four side faces substantially perpendicular to the rectangular bases where the rectangular bases are the end surfaces of the deformation-suppressing block 81 b which face the side plates 50 c and 50 d , and the side faces are the side surfaces of the deformation-suppressing block 81 b which extend in the axial direction of the outer rotor 51 .
- the jointing of the resinous block 81 a and the deformation-suppressing block 81 b of the seal functioning portion 81 may be changed from the one, as illustrated in FIGS. 3( b ) and 3 ( c ).
- the following discussion will refer to the case where the deformation-suppressing block 81 b is, as illustrated in FIG. 7 , of a quadrangular prism shape, but however, the same joining structure as described below may be used in the case where the deformation-suppressing block 81 b is substantially of a triangular prism shape, as illustrated in FIG. 5 , or a circular cylindrical shape, as illustrated in FIG. 6 .
- the resinous block 81 a has formed on the surface thereof a protrusion 81 ac which projects toward the low-pressure region of the gap S.
- the deformation-suppressing block 81 b is shaped to have a recess 81 bb which is shaped to have a depth, as can be seen from FIG. 8( b ), substantially extending from the side of the high-pressure region to the side of the low-pressure region of the gap S.
- the recess 81 bb is recessed from the side of the high-pressure region to the side of the low-pressure region of the gap S.
- the protrusion 81 ac is fit in the recess 81 bb to establish the mechanical joint between the resinous block 81 a and the deformation-suppressing block 81 b.
- the jointing of the resinous block 81 a and the deformation-suppressing block 81 b of the seal functioning portion 81 may alternatively be established in the way, as illustrated in FIGS. 9( a ) and 9 ( b ).
- the deformation-suppressing block 81 b has a protrusion 81 ba formed on two of the side surfaces thereof which face the resinous block 81 a (i.e., the side surfaces of the deformation-suppressing block 81 b which contact the resinous block 81 a )
- the protrusion 81 ba is of a U-shaped in traverse cross section and extends from the corner of the deformation-suppressing block 81 b which faces the outer rotor 51 to the corner of the deformation-suppressing block 81 b which faces a portion of the inner wall of the recess 50 e which is closer to the low-pressure region of the gap S.
- the resinous block 81 a has formed therein a recess or groove 81 ab which extends from the surface thereof which faces the outer rotor 51 and to the surface thereof which faces the portion of the inner wall of the recess 50 e which is closer to the low-pressure region of the gap S.
- the groove 81 ab is formed in the surface of the resinous block 81 a which faces the deformation-suppressing block 81 b .
- the groove 81 ab is of a U-shaped in traverse cross section.
- the protrusion 81 ba of the deformation-suppressing block 81 b is fit in the groove 81 ab of the resinous block 81 a to establish the mechanical joining of the resinous block 81 a and the deformation-suppressing block 81 b.
- the jointing of the resinous block 81 a and the deformation-suppressing block 81 b of the seal functioning portion 81 may alternatively be established in the way, as illustrated in FIGS. 10( a ) and 10 ( b ).
- the deformation-suppressing block 81 b has a semi-cylindrical protrusion 81 bc formed on one of the corners thereof which face the resinous block 81 a .
- the protrusion 81 bc is formed on the surface of the deformation-suppressing block 81 b which contacts the resinous block 81 a .
- the resinous block 81 a has a semi-cylindrical recess or groove 81 ad formed in the inner corner thereof which faces the deformation-suppressing block 81 b .
- the groove 81 ad is formed in the surface of the resinous block 81 a which faces the deformation-suppressing block 81 b .
- the protrusion 81 bc of the deformation-suppressing block 81 b is fit in the groove 81 ad of the resinous block 81 a to establish the mechanical joining of the resinous block 81 a and the deformation-suppressing block 81 b.
- the jointing of the resinous block 81 a and the deformation-suppressing block 81 b of the seal functioning portion 81 may alternatively be established, as illustrated in FIG. 11 , by embedding at least a portion of the deformation-suppressing block 81 b in the resinous block 81 a .
- the side surface of the resinous block 81 a which faces the deformation-suppressing block 81 b is partially wrapped around the side surfaces of the deformation-suppressing block 81 b to establish the mechanical joint between the resinous block 81 a and the deformation-suppressing block 81 b.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Regulating Braking Force (AREA)
- Valves And Accessory Devices For Braking Systems (AREA)
- Rotary Pumps (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
Abstract
Description
- The present application claims the benefit of priority of Japanese Patent Application No. 2014-22442 filed on Feb. 7, 2014, the disclosure of which is incorporated herein by reference.
- 1.Technical Field of the Invention
- This disclosure relates generally to a rotating pump designed to suck and then discharge fluid, and more particularly to such a rotating pump which is useful for a brake system working to suck and discharge brake fluid to regulate the pressure thereof for controlling the braking force.
- 2. Background Art
- Japanese Patent First Publication No. 2002-295376 teaches use of an internal gear pump, such as a trochoid pump, as a rotating pump for an automotive brake system. This type of rotating pump is made up of an inner rotor, an outer rotor, and a casing. The inner rotor is equipped with outer teeth formed on an outer periphery thereof. The outer rotor is equipped with inner teeth formed on an inner periphery thereof. The outer and inner rotors are mounted in the casing. Specifically, within the casing, the teeth of the inner rotor mesh with those of the outer rotor to define a plurality of cavities (i.e., clearances). If a line passing through the centers of the inner rotor and the outer rotor is defined as the center line of the pump, the pump has an inlet port (i.e., a suction side) and an outlet port (i.e., a discharge side) which are diametrically opposed to each other across the center line of the pump.
- In operation of the pump, the inner rotor is rotated by a drive shaft, so that the outer rotor is rotated in the same direction as the inner rotor through the meshing of the outer teeth and the inner teeth. This causes the volumes of the cavities to increase and then decrease continuously to suck fluid from the inlet port and then discharge it from the outlet port every 360° rotation of the outer and inner rotors.
- During the operation of the pump, gaps between the outer periphery of the outer rotor and the casing are broken down into a low-pressure region and a high-pressure region. A sealing member is, therefore, disposed on the outer periphery of the outer rotor to hermetically isolate the low-pressure and high-pressure regions from each other. Specifically, the casing has two cavities formed on portions of the inner circumference thereof which face the outer circumference of the outer rotor. Sealing mechanisms each made up of a resin member and a rubber member are disposed in the cavities, respectively. The rubber member is placed on the bottom of the cavity of the casing, while the resin member is laid between the rubber member and the outer rotor. The rubber member, thus, presses the resin member into constant abutment with the peripheral surface of the outer rotor to hermetically seal between the low-pressure region and the high-pressure region.
- In recent years, there has been an increasing demand for the pump to discharge brake fluid at high pressure. The above described conventional sealing mechanisms, however, need to have a large clearance between the casing and the outer rotor for meeting a pressure requirement because of design limitations in terms of production tolerance of the pump. It is, therefore, impossible for the pump to have the required endurance against the discharge of the brake fluid at high pressure. For instance, the resin member may deform into the clearance between the casing and the outer rotor, thereby resulting in breakage of the resin member, which leads to a lack of sealing ability of the sealing mechanism. Usually, the resin member is easy to deform, especially, at high temperature and high pressure, thereby facilitating the deformation thereof into the clearance between the casing and the outer rotor. It is, thus, difficult to ensure the durability of the sealing mechanisms and achieve the discharging of the brake fluid at high pressure.
- It is therefore an object of this disclosure to provide an improved structure of a rotating pump designed to ensure a required degree of hermetic sealing and capable of discharging fluid at high pressure.
- According to one aspect of the invention, there is provided a rotating pump which may be employed in a brake system for automotive vehicles. The rotating pump comprises: (a) a drive shaft; (b) a rotor assembly made up of an outer rotor and an inner rotor, the outer rotor having inner teeth formed on an inner periphery thereof, the inner rotor having outer teeth formed on an outer periphery thereof and being rotated by the drive shaft around an axis defined by the drive shaft, the outer teeth meshing with the inner teeth of the outer rotor to define a plurality of cavities; (c) a casing in which the drive shaft is installed, the casing including a rotor chamber in which the rotor assembly is mounted to be rotatable with a gap formed between an inner peripheral surface of the casing which faces the outer rotor and an outer peripheral surface of the outer rotor, the casing having an inlet port from which fluid is sucked into the rotor assembly and an outlet port from which the fluid is discharged with rotation of the rotor assembly; (d) a first and a second recess formed in the inner peripheral surface of the casing which is exposed to the gap; and (f) a first and a second sealing member which are disposed in the first and second recesses, respectively, to define within the gap a low-pressure region leading to the inlet port and a high-pressure region leading to the outlet port. Each of the first and second sealing members is made up of a seal functioning portion and an elastically pressing portion. The seal functioning portion is placed in contact with the outer periphery of the outer rotor and a low-pressure side surface that is a portion of an inner wall surface of a corresponding one of the first and second recesses which is closer to the low-pressure region than to the high-pressure region to establish a difference in pressure between the low-pressure region and the high-pressure region. The elastically pressing portion is located closer to a bottom of a corresponding one of the first and second recesses than the seal functioning portion is and works to press the seal functioning portion against the outer periphery of the outer rotor. The seal functioning portion includes a resinous member and a deformation-suppressing member. The resinous member is placed in contact with the outer periphery of the outer rotor and the low-pressure side surface of the inner wall surface of a corresponding one of the first and second recesses to establish the difference in pressure between the low-pressure region and the high-pressure region. The deformation-suppressing member is made of material which is more rigid than that of the resinous member and located closer to the low-pressure region than the resinous member is. A boundary between a surface of the deformation-suppressing member which faces the low-pressure side surface and a surface of the resinous member which faces the low-pressure side surface is located inside a corresponding one of the recesses.
- The first and second sealing members are, as described above, installed in the casing to hermetically isolate between the low-pressure region and the high-pressure region in the gap. Specifically, the seal functioning portion of each of the first and second sealing members is pressed by an elastically reactive force, as produced by the elastically pressing portion, and the high pressure of the fluid in the gap toward the low-pressure region in the gap, thereby bringing the resinous member into constant abutment with the inner wall of a corresponding of the first and second recesses in addition to the outer periphery of the outer rotor and an inner wall of the casing to establish a hermetic seal between the high-pressure region and the low-pressure region in the gap.
- The resinous member is pressed by the high pressure of the fluid, but stopped by the deformation-suppressing member of the seal functioning portion from being deformed into the low-pressure region of the gap, thereby minimizing the risk of breakage of the resinous member to ensure the stability of sealing the gap. This enables the rotating pump to discharge the fluid at an increased pressure.
- The present invention will be understood more fully from the detailed description given hereinbelow and from the accompanying drawings of the preferred embodiments of the invention, which, however, should not be taken to limit the invention to the specific embodiments but are for the purpose of explanation and understanding only.
- In the drawings:
-
FIG. 1 is a circuit diagram which illustrates a brake system equipped with a rotating pump according to the first embodiment of the invention; -
FIG. 2 is a partially sectional view which illustrates an internal structure of the rotating pump ofFIG. 1 ; -
FIG. 3( a) is an enlarged view of a sealing member shown inFIG. 2 ; -
FIG. 3( b) is an illustration which shows a seal functioning portion of a sealing member, as viewed in an axial direction of a drive shaft of the rotating pump ofFIG. 2 ; -
FIG. 3( c) is an illustration of the seal functioning portion ofFIG. 3( b), as viewed from the center of the rotating pump in a radius direction of the drive shaft; -
FIG. 4 is an illustration which shows layout of the sealing member shown inFIG. 2 , as viewed from the center of the rotating pump in a radius direction of a drive shaft of the rotating pump; -
FIG. 5 is an illustration which shows a first modification of a sealing member, as viewed in an axial direction of a drive shaft of the rotating pump ofFIG. 2 ; -
FIG. 6 is an illustration which shows a second modification of a sealing member, as viewed in an axial direction of a drive shaft of the rotating pump ofFIG. 2 ; -
FIG. 7 is an illustration which shows a third modification of a sealing member, as viewed in an axial direction of a drive shaft of the rotating pump ofFIG. 2 ; -
FIG. 8( a) is an illustration which shows a first modification of a joining structure of a resinous member and a deformation-suppressing member of a sealing member, as viewed in an axial direction of a drive shaft of the rotating pump ofFIG. 2 ; -
FIG. 8( b) is a sectional illustration of the joining structure inFIG. 8( a), as viewed from the center of the rotating pump in a radius direction of the drive shaft; -
FIG. 9( a) is an illustration which shows a second modification of a joining structure of a resinous member and a deformation-suppressing member of a sealing member, as viewed in an axial direction of a drive shaft of the rotating pump ofFIG. 2 ; -
FIG. 9( b) is a sectional illustration of the joining structure inFIG. 9( a), as viewed in a radius direction of the drive shaft; -
FIG. 10( a) is an illustration which shows a third modification of a joining structure of a resinous member and a deformation-suppressing member of a sealing member, as viewed in an axial direction of a drive shaft of the rotating pump ofFIG. 2 ; -
FIG. 10( b) is a sectional illustration of the joining structure inFIG. 10( a), as viewed in a radius direction of the drive shaft; and -
FIG. 11 is an illustration which shows a fourth modification of a joining structure of a resinous member and a deformation-suppressing member of a sealing member, as viewed in an axial direction of a drive shaft of the rotating pump ofFIG. 2 . - Embodiments will be described below with reference to the drawings wherein like reference numbers refer to like or equivalent parts in several views.
- Referring to
FIG. 1 , there is shown an automotive brake system equipped with a rotating pump that is a part of a hydraulic circuit of the brake system. The brake system, as referred to herein, is designed as a so-called diagonal split system which includes two brake hydraulic circuits one of which controls the right front and the left rear wheel and the other of which controls the left front and the right rear wheel, but may be engineered as a front/rear split system. - The brake system is equipped with a brake pedal 1 (i.e., a brake actuating member) to be depressed by a vehicle occupant or driver for applying the brakes to the vehicle, a
brake booster 12, amaster cylinder 3,wheel cylinders pressure control actuator 6. Themaster cylinder 3, as will be described later in detail, works to produce a braking hydraulic pressure in response to an operation of the brake actuating member (i.e., the brake pedal 1). - The brake pedal 1 is connected to the
brake booster 2 and themaster cylinder 3. When the driver of the vehicle depresses the brake pedal 1, thebrake booster 2 works to boost the pressure applied to the brake pedal 1. Specifically, thebrake booster 2 is equipped with a push rod which works to push master pistons installed in themaster cylinder 3, thereby developing the pressure (which will also be referred to as M/C pressure below). - To the
master cylinder 3, amaster reservoir 3 a is connected which stores therein an excess of the brake fluid in themaster cylinder 3. - The M/C pressure is transmitted to the front
right wheel cylinder 4 and the rearleft wheel cylinder 5 as wheel cylinder (W/C) pressure. The brakepressure control actuator 6 is disposed between themaster cylinder 3 and thewheel cylinders wheel cylinders - The brake
pressure control actuator 6 includes a first hydraulic circuit and a second hydraulic circuit. The first hydraulic circuit is a hydraulic circuit working to control the brake fluid to be applied to the front right wheel FR (i.e., the wheel cylinder 4) and the left rear wheel RL (i.e., the wheel cylinder 5). The second hydraulic circuit is a hydraulic circuit working to control the brake fluid to be applied to the left front wheel FL and the right rear wheel RR. The first hydraulic circuit and the second hydraulic circuit are substantially identical in structure with each other. The following discussion will refer only to the first hydraulic circuit for the brevity of disclosure. - The brake system (i.e., the first hydraulic circuit) is equipped with a main hydraulic line A (also called a main hydraulic path below) connecting with the
master cylinder 3. The main hydraulic line A has disposed therein a differentialpressure control valve 7 which divides the main hydraulic line A into two: a pipe line A1 which is a hydraulic line extending from themaster cylinder 3 to the differentialpressure control valve 7 and subjected to the M/C pressure and a pipe line A2 which is a hydraulic line extending from the differentialpressure control valve 7 to thewheel cylinders - The differential
pressure control valve 7 is operable in either of two modes: an open mode and a pressure-difference mode. In a normal braking mode where it is required to produce the braking force as a function of an amount of depression of thebrake pedal 11 by the driver, the valve position of the differentialpressure control valve 7 is placed in the open mode. When the valve position of the differentialpressure control valve 7 is placed in the pressure-difference mode, the differentialpressure control valve 7 works to control the flow of the braking fluid to elevate and hold the W/C pressures above the M/C pressure by a pressure difference, as developed by the differentialpressure control valve 7. - The pipe line A2 includes two branch lines: one being equipped with a pressure-increasing
valve 8 a which increases the pressure of the brake fluid supplied to thewheel cylinder 4, and one being equipped with a pressure-increasingvalve 8 b which increases the pressure of the brake fluid supplied to thewheel cylinder 5. - Each of the pressure-increasing
valves wheel cylinder 4 or 5). Specifically, when the pressure-increasingvalve 8 a is opened, the pressure of the brake fluid, as created by the M/C pressure, is transmitted to thewheel cylinder 4. In a normal braking mode where brake fluid pressure control, such as an anti-lock brake control, is not executed, the pressure-increasingvalve 8 a is opened. The same is true for the pressure-increasingvalve 8 b. - The brake
pressure control actuator 6 also includes a hydraulic line B which extends as a pressure-reducing path between apressure control reservoir 9 and a junction of the pressure-increasingvalve 8 a and thewheel cylinder 4 and between thepressure control reservoir 9 and a junction of the pressure-increasingvalve 8 b and thewheel cylinder 5. The brake fluid is drained to thepressure control reservoir 9 through the hydraulic line B to control the W/C pressure exerted on thewheel cylinders - The hydraulic line B is equipped with pressure-reducing
valves valves wheel cylinder 4 or 5). In the normal braking mode where the brake fluid pressure control is not executed, the pressure-reducingvalves pressure control reservoir 9, the pressure-reducingvalves - The brake
pressure control actuator 6 also includes a hydraulic line C which extends between thepressure control reservoir 9 and the hydraulic line A. The hydraulic line C is equipped with apump 11 which is disposed between a junction of the differentialpressure control valve 7 and the pressure-increasingvalves electric motor 12. The hydraulic line C also hascheck valves pump 11. - The hydraulic line C is also equipped with an
accumulator 13 disposed downstream of thepump 11 to alleviate pulsation of the brake fluid discharged from thepump 11. The brakepressure control actuator 6 also includes a hydraulic line D which extends as a sub-hydraulic line between thepressure control reservoir 9 and themaster cylinder 3. Thepump 11 works to suck the brake fluid from the hydraulic line A1 through the hydraulic line D and thepressure control reservoir 9 and output it to the hydraulic line A2 to elevate the W/C pressures. - The second hydraulic circuit, as already described, has the same structure as described above as that of the first hydraulic circuit. The
control valves pump 11, thepressure control reservoir 9, and themotor 12 are installed in a housing which is drilled to define the above described hydraulic lines and constitute the brakepressure control actuator 6. The brakepressure control actuator 6 is, as described above, disposed between themaster cylinder 3 and thewheel cylinders FIG. 1 . - The brake system works to execute brake fluid pressure control tasks such as the ABS control, the brake assist control, the adaptive cruise control, and the regenerative braking control and drive the rotating
pump 11 to suck or discharge the brake fluid. In recent years, it has been required to develop the high W/C pressure quickly; for example, in the brake assist control mode or the adaptive cruise control mode where it is necessary to actuate therotating pump 11 to create a high pressure of brake fluid. The discharge pressure of therotating pump 11 is, thus, required to be increased. - In order to meet the above requirement, the rotating
pump 11 of this embodiment is engineered in the following way. The structure of therotating pump 11 will be described in detail with reference toFIGS. 2 , 3, and 4. - The
rotating pump 11 is installed in arotor chamber 50 a of acasing 50. Specifically, within therotor chamber 50 a, anouter rotor 51 and aninner rotor 52 are arranged with center axes X and Y thereof being eccentric from each other. A combination of theouter rotor 51 and theinner rotor 52 works as a rotor assembly in therotating pump 11. - The
outer rotor 51 hasinner teeth 51 a formed on an inner periphery thereof. Theinner rotor 52 hasouter teeth 52 a formed on an outer periphery thereof. Theinner teeth 51 a of theouter rotor 51 mesh with theouter teeth 52 a of theinner rotor 52 so as to create a plurality of gaps orenclosed cavities 53 therebetween. More specifically, surfaces of theinner teeth 51 a and theouter teeth 52 a are placed in contact with each other to define thecavities 53. Theouter rotor 51 and theinner rotor 52 are rotated by adrive shaft 54 arranged in the center of theinner rotor 52, so that thecavities 53 are changed in volume thereof with rotation of thedrive shaft 54, thereby sucking or discharging the brake fluid. - The thus constructed
rotating pump 11 is a multi-tooth trochoid pump with no crescent in which theinner teeth 51 a of theouter rotor 51 and theouter teeth 52 a of theinner rotor 52 mesh with each other to define thecavities 53. The meshing surfaces of theouter teeth 52 a contact at a plurality of points with those of theinner teeth 51 a to transmit torque from theinner rotor 52 to theouter rotor 51. - The
casing 50 includes acenter plate 50 b andside plates FIG. 4 . Thecenter plate 50 b embraces the outer peripheries of therotors side plates rotors center plate 50 b. Thecenter plate 50 b and theside plates rotor chamber 50 a. Theside plates drive shaft 54 is fit. Theouter rotor 51 and theinner rotor 52 are disposed to be rotatable within therotor chamber 50 a. In other words, a rotatable assembly of theouter rotor 51 and theinner rotor 52 is arranged rotatably in therotor chamber 50 a of thecasing 50, so that theouter rotor 51 may rotate about the axis X, and theinner rotor 52 may rotate about the axis Y. The axis Y is an axis of rotation of theinner rotor 52 defined by the drive shaft 54 (i.e., a longitudinal center line of the drive shaft 54). - If a line traversing perpendicular to the axes X and Y of the
outer rotor 51 and theinner rotor 52 is, as illustrated inFIG. 2 , defined as the center line Z of therotating pump 11, theside plate 50 c has aninlet port 60 and anoutlet port 61 which are located on the left and right sides of the center line Z and communicate with therotor chamber 50 a. Theinlet port 60 communicates with some of thecavities 53 through which the brake fluid is sucked into thepump 11. Theoutlet port 61 which communicates with some of thecavities 53 through which the brake fluid is discharged from thepump 11. - The
enclosed cavity 53 a that is one of thecavities 53 which has the greatest volume does not communicate with theinlet port 60 or with theoutlet port 61. Thecavity 53 a works to develop a difference between the suction pressure in theinlet port 60 and the discharge pressure in theoutlet port 61. One of theside plates outer rotor 51, that is, a clearance between the outer periphery of theouter rotor 51 and the inner wall of the casing 50 (i.e., the inner wall of therotor chamber 50 a) and theinlet port 60, while the second flow path communicates between the gap S and theoutlet port 61. This creates a low-pressure region, as defined by a portion of the gap S, as will be described later in detail, communicating with theinlet port 60, and a high-pressure region, as defined by a portion of the gap S communicating with theoutlet port 61. In practice, the gap S is, as can be seen inFIG. 2 , blocked on the side of theoutlet port 61. - The
center plate 50 b of thecasing 50, as clearly illustrated inFIG. 2 , hasrecesses recesses recesses inlet port 60 around the axis Y (i.e., the rotating center) of theouter rotor 51. In other words, each of therecesses Sealing members recesses outer rotor 51. In other words, the sealingmembers outer rotor 51 through a portion of the gap S which faces and communicates with theinlet port 60. The sealingmembers - The sealing
members members inlet port 60 at the suction pressure and a portion of the gap S which communicates with theoutlet port 61 at the discharge pressure, thereby developing a balance in pressure between outside and inside theouter rotor 51. This prevents theouter rotor 51 from being pressed by the pressure of the brake fluid locally against theinner rotor 52 and thecasing 50, thereby minimizing irregular wear of theteeth outer rotor 51. -
FIGS. 3( a) to 3(c) illustrate the structure of the sealingmember 80 in detail. The sealingmember 90 is identical in structure with the sealingmember 80. The following discussion will, thus, refer only to the sealingmember 80 for the sake of simplicity of explanation. - The sealing
member 80 is, as can be seen inFIGS. 3( a) to 3(c), made up of two parts: aseal functioning portion 81 and an elastically pressingportion 82. - The
seal functioning portion 81 is pressed against the circumferential surface of theouter rotor 51 and theside plates seal functioning portion 81 is made up of aresinous block 81 a and a deformation-suppressingblock 8 b. Theseal functioning portion 81 is substantially of a pentagonal prism shape. The main part of theseal functioning portion 81 is made of theresinous block 81 a, while the other part of theseal functioning portion 81 is made of the deformation-suppressingblock 81 b to define a surface of theseal functioning portion 81 exposed to the low-pressure region of the gap S. In other words, the deformation-suppressingblock 81 b is arranged so as to define a portion of theseal functioning portion 81 which is exposed to the low-pressure region of the gap S, while theresinous block 81 a is shaped or located so as not to be exposed to the low-pressure region of the gap S. - The
resinous block 81 a is made of a soft resin such as Teflon (Trade Mark). Theresinous block 81 a is shaped to have outer surfaces contacting the outer circumference of the outer rotor 51 (seeFIG. 3( a)), theside plates FIG. 4) , and the inner wall surface of therecess 50 e, i.e., a portion (which will also be referred to as a low-pressure side surface below) of the inner wall of therecess 50 e which is closer to the low-pressure side than to the high-pressure side in the gap S. The circumference (i.e., the outer peripheral surface) and the side surfaces of the deformation-suppressingblock 81 b are substantially entirely enclosed or surrounded by the surfaces of therecess 50 e, theresinous block 81 a, theside plates outer rotor 51, thereby hermetically isolating between the high-pressure region and the low-pressure region in the gap S to develop a desired difference in pressure between the high-pressure region and the low-pressure region. Theresinous block 81 a is shaped to have a dimension (i.e., length L1 inFIG. 4 ) in the same direction as the axial direction of the outer rotor 51 (i.e., a direction parallel to the axis of rotation of the inner rotor 52) which is set greater than the thickness of therotor chamber 50 a in the axial direction of the outer rotor 51 (i.e., an interval between the side surfaces of theside plates resinous block 81 a, as indicated by a broken line inFIG. 4 , to be elastically squeezed or deformed, so that the length (i.e., the dimension in the vertical direction inFIG. 4 ) of theresinous block 81 a is decreased, thereby enhancing the ability to seal the gap S. - The
resinous block 81 a is also shaped to have theflat surface 81 aa, as illustrated inFIGS. 3( a) and 3(b), which is diagonally opposed to the surface thereof with which the deformation-suppressingblock 81 b is placed in contact. Thesurface 81 aa may be formed to extend substantially parallel to the surface the deformation-suppressingblock 81 b contacts. The elastically pressingportion 82 of the sealingmember 80 is urged into abutment with thesurface 81 aa of theresinous block 81 a. - The deformation-suppressing
block 81 b is made from material such as resin or metal which is more rigid than theresinous block 81 a and works as a stopper to stop theresinous block 81 a from elastically deforming toward the gap S. Specifically, the deformation-suppressingblock 81 b is located to be exposed to the low-pressure region of the gap S. In other words, the deformation-suppressingblock 81 b lies at a portion of theseal functioning portion 81 which is exposed to the low-pressure region of the gap S, so that theresinous block 81 a is not exposed to the low-pressure region. - The deformation-suppressing
block 81 b is formed in the shape of a triangular prism made of two triangular bases and three side faces where the triangular bases are the end surfaces of the deformation-suppressingblock 81 b which face theside plates block 81 b which extend in the axial direction of theouter rotor 51. The deformation-suppressingblock 81 b is dimensionally formed so that one of the side surfaces thereof partially faces or is partially exposed to the gap S, and aboundary 100, as illustrated inFIG. 3( a), between the one of the side surfaces and the surface of theresinous block 81 a lies inside therecess 50 e. The deformation-suppressingblock 81 b is also shaped to have a dimension (i.e., length L2) in the same direction as the axial direction of the outer rotor 51 (i.e., a direction parallel to the axis of rotation of the inner rotor 52) which is, as can be seen fromFIG. 4 , set smaller than the thickness of therotor chamber 50 a in the axial direction of the outer rotor 51 (i.e., the minimum interval between the side surfaces of theside plates - The
resinous block 81 a and the deformation-suppressingblock 81 b may be mechanically joined together or separate from each other. In this embodiment, they are joined together. Specifically, theresinous block 81 a, as illustrated inFIG. 3( c), has a wedge-shapedrecess 81 ab formed in the surface thereof which diagonally faces theouter rotor 51. The wedge-shapedrecess 81 ab is shaped to have a depth, as can be seen fromFIG. 3( b), substantially extending from the side of the low-pressure region to the side of the high-pressure region of the gap S. In other words, the wedge-shapedrecess 81 ab is recessed from the side of the low-pressure region to the side of the high-pressure region of the gap S. The deformation-suppressingblock 81 b is shaped to have a wedge-shapedprotrusion 81 ba formed on the surface thereof which faces theresinous block 81 a. The wedge-shapedprotrusion 81 ba projects toward the high-pressure region of the gap S. The wedge-shapedprotrusion 81 ba is fit in the wedge-shapedrecess 81 ab to establish the joint of theresinous block 81 a and the deformation-suppressingblock 81 b. - The
seal functioning portion 81 is made up of theresinous block 81 a and the deformation-suppressingblock 81 b in the above way. - The elastically pressing
portion 82 is made of an elastically deformable material such as rubber and located deeper than theseal functioning portion 81 within therecess 50 e, in other words, closer to the bottom of therecess 50 e than theseal functioning portion 81 is. The elastically pressingportion 82 is elastically deformed within therecess 50 e, thereby creating a reactive force which presses theresinous block 81 a of theseal functioning portion 81 against the outer wall surface of theouter rotor 51 and the inner wall surface of therecess 50 e. In other words, the elastically pressingportion 82 is elastically deformed between the inner wall surface of therecess 50 e and thesurface 81 aa of theresinous block 81 a of theseal functioning portion 81, thereby pressing thesurface 81 a a to urge theresinous block 81 a against the inner wall of therecess 50 e and the outer circumference of theouter rotor 51. This establishes a liquid-tight seal in the gap S, that is, hermetically blocks the gap S to isolate between the high-pressure region and the low-pressure region. - The operations of the brake system and the
rotating pump 11 will be described below. For instance, when one of the above described brake fluid pressure control tasks is initiated, thecontrol valves 7 and 30 to 33 are actuated according to the control mode, as specified by the one of the brake fluid pressure control tasks. Simultaneously, themotor 12 is actuated to suck and then discharge the brake fluid through thepump 11. - Specifically, when the
motor 12 is actuated, theinner rotor 51 of thepump 11 is rotated by thedrive shaft 54, thereby rotating theouter rotor 51 in the same direction as theinner rotor 51 through the meshing of theinner teeth 51 a with theouter teeth 52 a. The volumes of thecavities 53 are changed sequentially every rotation of theouter rotor 51 and theinner rotor 52, thereby sucking the brake fluid from theinlet port 60 and then discharge it from theoutlet port 61 to the hydraulic line A2 to elevate the W/C pressure. - In the above way, the rotating
pump 11 performs a normal pumping operation in which therotors inlet port 60 and then discharge it from theoutlet port 61. During the normal pumping operation, a portion of the gap S on the outer circumference of theouter rotor 51 communicating with theinlet port 60 is kept at the suction pressure, while a portion of the gap S communicating with theoutlet port 61 is kept at the discharge pressure. This creates, as described above, the low-pressure region and the high-pressure region in the gap S. - The sealing
members center plate 50 b of thecasing 50 to hermetically isolate between the low-pressure region and the high-pressure region in the gap S. Specifically, theseal functioning portion 81 of each of the sealingmembers portion 82, and the high pressure of the brake fluid in the gap S toward the low-pressure region in the gap S, thereby bringing theresinous block 81 a into constant abutment with the inner wall of therecess 50 e in addition to the outer circumferential surface of theouter rotor 51 and the surfaces of theside plates - The
resinous block 81 a is pressed by the high pressure of the brake fluid, but stopped by the deformation-suppressingblock 81 b of theseal functioning portion 81 from being deformed into the low-pressure region of the gap S, thereby minimizing the risk of breakage of theresinous block 81 a to ensure the stability of sealing the gap S. This enables therotating pump 11 to discharge the brake fluid at an increased pressure. - While the present invention has been disclosed in terms of the preferred embodiment in order to facilitate better understanding thereof, it should be appreciated that the invention can be embodied in various ways without departing from the principle of the invention.
- For instance, the
seal functioning portion 81 of each of the sealingmembers resinous block 81 a and the deformation-suppressingblock 81 b which are mechanically separate from each other. In this case, it is also advisable that at least theboundary 100 between one of the side surfaces of the deformation-suppressingblock 81 b which is exposed to the low-pressure region of the gap S and the surface of theresinous block 81 a which faces in the same direction as the one of the side surfaces of the deformation-suppressingblock 81 b be located fully within a corresponding one of therecesses - The deformation-suppressing
block 81 b may be, as illustrated inFIG. 6 , formed in the shape of a circular cylinder made of two circular bases and a side face substantially perpendicular to the circular bases where the circular bases are the end surfaces of the deformation-suppressingblock 81 b which face theside plates block 81 b which extends in the axial direction of theouter rotor 51. In this case, when therotating pump 11 is at rest in operation, theresinous block 81 a is located far away from the deformation-suppressingblock 81 b on a portion of the inner surface of, for example, therecess 50 e which is closer to the low-pressure region than to the high-pressure region of the gap S, thus facilitating the ease of elastic deformation of theresinous block 81 a into the gap S. This problem, however, may be alleviated by making the deformation-suppressingblock 81 b to have a radius greater than the thickness of the gap S (i.e., the dimension of the gap S in the radius direction of the outer rotor 50). In other words, it is advisable that the deformation-suppressingblock 81 b be shaped so that a boundary between theresinous block 81 a and the deformation-suppressingblock 81 b on a portion of the inner wall of, for example, therecess 50 e which is closer to the low-pressure region than to the high-pressure region fully lies, like in the first embodiment, inside therecess 50 e when theresinous block 81 a is deformed most greatly. The same applies to the case where the deformation-suppressingblock 81 b is of a shape other than the triangular prism or the circular cylinder. Specifically, the deformation of theresinous block 81 a into the gap S is avoided by making the deformation-suppressingblock 81 b to have a dimension greater than that of the gap S in the radius direction of the drive shaft 54 (i.e., the outer rotor 51) so that the deformation-suppressingblock 81 b is at least partially placed in contact with the inner wall of therecess 50 e. - The deformation-suppressing
block 81 b may alternatively be, as illustrated inFIG. 7 , formed in the shape of a quadrangular prism made of two square or rectangular bases and four side faces substantially perpendicular to the rectangular bases where the rectangular bases are the end surfaces of the deformation-suppressingblock 81 b which face theside plates block 81 b which extend in the axial direction of theouter rotor 51. - The jointing of the
resinous block 81 a and the deformation-suppressingblock 81 b of theseal functioning portion 81 may be changed from the one, as illustrated inFIGS. 3( b) and 3(c). The following discussion will refer to the case where the deformation-suppressingblock 81 b is, as illustrated inFIG. 7 , of a quadrangular prism shape, but however, the same joining structure as described below may be used in the case where the deformation-suppressingblock 81 b is substantially of a triangular prism shape, as illustrated inFIG. 5 , or a circular cylindrical shape, as illustrated inFIG. 6 . - Specifically, the
resinous block 81 a, as illustrated inFIGS. 8( a) and 8(b), has formed on the surface thereof aprotrusion 81 ac which projects toward the low-pressure region of the gap S. The deformation-suppressingblock 81 b is shaped to have arecess 81 bb which is shaped to have a depth, as can be seen fromFIG. 8( b), substantially extending from the side of the high-pressure region to the side of the low-pressure region of the gap S. In other words, therecess 81 bb is recessed from the side of the high-pressure region to the side of the low-pressure region of the gap S. Theprotrusion 81 ac is fit in therecess 81 bb to establish the mechanical joint between theresinous block 81 a and the deformation-suppressingblock 81 b. - The jointing of the
resinous block 81 a and the deformation-suppressingblock 81 b of theseal functioning portion 81 may alternatively be established in the way, as illustrated inFIGS. 9( a) and 9(b). Specifically, the deformation-suppressingblock 81 b has aprotrusion 81 ba formed on two of the side surfaces thereof which face theresinous block 81 a (i.e., the side surfaces of the deformation-suppressingblock 81 b which contact theresinous block 81 a ) Theprotrusion 81 ba is of a U-shaped in traverse cross section and extends from the corner of the deformation-suppressingblock 81 b which faces theouter rotor 51 to the corner of the deformation-suppressingblock 81 b which faces a portion of the inner wall of therecess 50 e which is closer to the low-pressure region of the gap S. Theresinous block 81 a has formed therein a recess or groove 81 ab which extends from the surface thereof which faces theouter rotor 51 and to the surface thereof which faces the portion of the inner wall of therecess 50 e which is closer to the low-pressure region of the gap S. In other words, thegroove 81 ab is formed in the surface of theresinous block 81 a which faces the deformation-suppressingblock 81 b. Thegroove 81 ab is of a U-shaped in traverse cross section. Theprotrusion 81 ba of the deformation-suppressingblock 81 b is fit in thegroove 81 ab of theresinous block 81 a to establish the mechanical joining of theresinous block 81 a and the deformation-suppressingblock 81 b. - The jointing of the
resinous block 81 a and the deformation-suppressingblock 81 b of theseal functioning portion 81 may alternatively be established in the way, as illustrated inFIGS. 10( a) and 10(b). Specifically, the deformation-suppressingblock 81 b has asemi-cylindrical protrusion 81 bc formed on one of the corners thereof which face theresinous block 81 a. In other words, theprotrusion 81 bc is formed on the surface of the deformation-suppressingblock 81 b which contacts theresinous block 81 a. Theresinous block 81 a has a semi-cylindrical recess or groove 81 ad formed in the inner corner thereof which faces the deformation-suppressingblock 81 b. In other words, thegroove 81 ad is formed in the surface of theresinous block 81 a which faces the deformation-suppressingblock 81 b. Theprotrusion 81 bc of the deformation-suppressingblock 81 b is fit in thegroove 81 ad of theresinous block 81 a to establish the mechanical joining of theresinous block 81 a and the deformation-suppressingblock 81 b. - The jointing of the
resinous block 81 a and the deformation-suppressingblock 81 b of theseal functioning portion 81 may alternatively be established, as illustrated inFIG. 11 , by embedding at least a portion of the deformation-suppressingblock 81 b in theresinous block 81 a. In other words, the side surface of theresinous block 81 a which faces the deformation-suppressingblock 81 b is partially wrapped around the side surfaces of the deformation-suppressingblock 81 b to establish the mechanical joint between theresinous block 81 a and the deformation-suppressingblock 81 b.
Claims (3)
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2014022442A JP2015148206A (en) | 2014-02-07 | 2014-02-07 | rotary pump |
JP2014-022442 | 2014-02-07 |
Publications (1)
Publication Number | Publication Date |
---|---|
US20150226212A1 true US20150226212A1 (en) | 2015-08-13 |
Family
ID=53774552
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US14/614,805 Abandoned US20150226212A1 (en) | 2014-02-07 | 2015-02-05 | Rotating pump |
Country Status (3)
Country | Link |
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US (1) | US20150226212A1 (en) |
JP (1) | JP2015148206A (en) |
CN (1) | CN104828061A (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN111828309A (en) * | 2019-04-23 | 2020-10-27 | 斯泰克波尔国际工程产品有限公司 | Vane pump |
US11988218B2 (en) | 2021-03-10 | 2024-05-21 | Multi Parts Supply Usa, Inc. | Electric coolant pump with expansion compensating seal |
Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20030080613A1 (en) * | 2001-10-29 | 2003-05-01 | Takahiro Yamaguchi | Rotary pump and braking apparatus using rotary pump |
US8702106B2 (en) * | 2006-07-20 | 2014-04-22 | Hydril Usa Manufacturing Llc | Pressure energized radial seal |
Family Cites Families (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2255817A5 (en) * | 1973-12-19 | 1975-07-18 | Dechavanne Jacques | |
JP3738568B2 (en) * | 1998-07-09 | 2006-01-25 | 株式会社デンソー | Brake device with rotary pump |
US6347843B1 (en) * | 1998-04-22 | 2002-02-19 | Denso Corporation | Pump equipment and method for assembling same |
-
2014
- 2014-02-07 JP JP2014022442A patent/JP2015148206A/en active Pending
-
2015
- 2015-02-05 US US14/614,805 patent/US20150226212A1/en not_active Abandoned
- 2015-02-06 CN CN201510064626.3A patent/CN104828061A/en active Pending
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20030080613A1 (en) * | 2001-10-29 | 2003-05-01 | Takahiro Yamaguchi | Rotary pump and braking apparatus using rotary pump |
US8702106B2 (en) * | 2006-07-20 | 2014-04-22 | Hydril Usa Manufacturing Llc | Pressure energized radial seal |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN111828309A (en) * | 2019-04-23 | 2020-10-27 | 斯泰克波尔国际工程产品有限公司 | Vane pump |
EP3959445A4 (en) * | 2019-04-23 | 2023-01-18 | Stackpole International Engineered Products, Ltd. | Vane pump with improved seal assembly for control chamber |
US11988218B2 (en) | 2021-03-10 | 2024-05-21 | Multi Parts Supply Usa, Inc. | Electric coolant pump with expansion compensating seal |
Also Published As
Publication number | Publication date |
---|---|
JP2015148206A (en) | 2015-08-20 |
CN104828061A (en) | 2015-08-12 |
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