JP4221843B2 - Rotary pump and brake device equipped with rotary pump - Google Patents

Rotary pump and brake device equipped with rotary pump Download PDF

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Publication number
JP4221843B2
JP4221843B2 JP28477899A JP28477899A JP4221843B2 JP 4221843 B2 JP4221843 B2 JP 4221843B2 JP 28477899 A JP28477899 A JP 28477899A JP 28477899 A JP28477899 A JP 28477899A JP 4221843 B2 JP4221843 B2 JP 4221843B2
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JP
Japan
Prior art keywords
portion
outer rotor
rotary pump
discharge port
rotor
Prior art date
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Expired - Fee Related
Application number
JP28477899A
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Japanese (ja)
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JP2000179466A (en
Inventor
卓 佐藤
智夫 原田
貴洋 山口
博之 新海
俊哉 森川
剛 渕田
Original Assignee
株式会社デンソー
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Priority to JP28422898 priority Critical
Priority to JP10-284228 priority
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Priority to JP28477899A priority patent/JP4221843B2/en
Publication of JP2000179466A publication Critical patent/JP2000179466A/en
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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00Rotary-piston machines or pumps
    • F04C2/08Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10Rotary-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
    • F04C2/102Rotary-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

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a rotary pump that sucks and discharges fluid and a brake device using the rotary pump, and is particularly suitable for application to an internal gear pump such as a trochoid pump.
[0002]
[Prior art]
An internal gear type rotary pump such as a trochoid pump is composed of an inner rotor having outer teeth on the outer periphery, an outer rotor having inner teeth on the inner periphery, a casing for housing these outer rotors and inner rotors, and the like. It is configured. The inner rotor and the outer rotor are arranged in the casing in a state where the inner teeth and the outer teeth are engaged with each other and a plurality of gaps are formed by these teeth.
[0003]
If the line passing through the central axes of the inner rotor and the outer rotor is the center line of the pump, suction ports and discharge ports communicating with the plurality of gaps are provided on both sides of the center line. When the pump is driven, the central axis of the inner rotor is used as a drive shaft, and the inner rotor rotates through the drive shaft, and the outer rotor is also rotated in the same direction due to the meshing of the outer teeth and the inner teeth. At this time, the volume of each gap portion changes in size while the outer rotor and the inner rotor make one rotation, and the oil is sucked from the suction port, and the oil is discharged from the discharge port.
[0004]
[Problems to be solved by the invention]
However, even if the inner rotor and the outer rotor are meshed in the rotational direction, the inner rotor and the outer rotor are configured so that they can move relative to each other in the axial direction of the drive shaft. There is a problem that the pump is driven in a state where the directions deviate from each other, and good pump performance cannot be obtained.
[0005]
The present invention has been made in view of the above problems, and an object of the present invention is to provide a rotary pump that can prevent the outer rotor and the inner rotor from being displaced from each other in the axial direction of the drive shaft and obtain good pump performance. And
[0006]
[Means for Solving the Problems]
By the way, conventionally, a rotary pump has a problem of oil leakage from the high-pressure outlet side to the low-pressure inlet side because a pressure difference is generated between the high-pressure outlet side and the low-pressure inlet side. .
[0007]
For this reason, for example, as shown in FIG. 6, the present inventors have a circle eccentric with respect to the drive shaft 54 in the gap between the axial end surfaces of the inner rotor 52 and the outer rotor 51 and the casing 50. By disposing an annular seal member 200 (two-dot chain line in the figure), the seal member 200 passes between the discharge port 61 and the drive shaft 54 so that the high-pressure discharge port 61 side and the low-pressure suction port The idea was to separate the 60 side.
[0008]
When such a seal member 200 is provided, the seal member 200 acts to hold down the inner rotor 52 and the outer rotor 51 at the closed portions 53a and 53b located between the discharge port 61 and the suction port 60. Therefore, it is considered that the deviation between the inner rotor 52 and the outer rotor 51 can be suppressed.
[0009]
However, portions of the seal member 200 that cover the closed portions 53a and 53b do not leak oil to the low-pressure suction port 60 side when the closed portions 53a and 53b communicate with the discharge port 61 to increase the pressure. If the inner rotor 52 and the outer rotor 51 are pressed down at this portion to prevent the inner rotor 52 and the outer rotor 51 from being displaced, the inner rotor 52 and the outer rotor 51 The wear caused by pressing down the rotor 51 deteriorates the durability of the seal member 200.
[0010]
Therefore, in order to achieve the above object, the following technical means are adopted.
[0011]
In the invention according to claims 1 to 7, the gap between the axial end surfaces of the inner rotor (52) and the outer rotor (51) and the casing (50) is provided between the discharge port and the drive shaft. The shaft of the drive shaft passes through the first and second closed portions (53a, 53b) and reaches the outer periphery of the outer rotor and is different from the portion passing through the first and second closed portions. It is characterized by comprising sealing means (100, 101) having adjusting portions (100A, 101A, 100B, 101B) for matching the positions of the inner rotor and outer rotor in the direction.
[0012]
In this way, the high pressure side and the low pressure side are sealed by providing the sealing means that passes between the discharge port and the drive shaft and extends to the outer periphery of the outer rotor through the first and second confinement portions. Can do. And, by providing an adjustment portion that matches the positions of the inner rotor and the outer rotor in the axial direction of the drive shaft in a portion different from the first and second confinement portions where sealing is required, It is possible to improve durability as a seal of a portion that seals the first and second confinement portions.
[0013]
Specifically, as shown in claim 2, a casing including a central plate (73) having a hole for accommodating the rotating portion, and first and second side plates (71, 72) sandwiching the central plate. Of these, the first and second side plates pass between the discharge port and the drive shaft, pass through the first and second confinement portions, reach the outer periphery of the outer rotor, and the first and second side plates. Grooves (71b, 72b) extending from the inner rotor to the outer rotor may be formed at a part different from the part that passes through the confinement part, and the sealing means may be disposed in the groove part.
[0014]
In the invention according to claim 3, the sealing means is made of an elastic body and is disposed on the bottom side of the groove portion, and the first sealing member (100a, 101a), and more than the first sealing member. And a second seal member (100b, 101b) disposed on the opening side of the groove portion. 2 The seal member is in contact with the inner rotor and the outer rotor.
[0015]
In this way, by pressing the second seal member with the first seal member made of an elastic body, the second seal member comes into contact with the inner rotor and the outer rotor and performs a sealing function. it can.
[0016]
According to a fourth aspect of the present invention, the adjustment portion can be configured to extend so as to overlap with the gap portion communicating with the discharge port or the suction port.
[0017]
Specifically, as shown in claim 5, in the sealing member, the annular portion that forms a substantially annular shape is arranged to be eccentric with respect to the drive shaft, and the annular portion is partially widened. Thereby, the adjustment part which overlaps with the space | gap part connected with the discharge port or the suction port can be comprised.
[0018]
The invention according to claim 7 is characterized in that an opening is formed in the adjustment portion, and the gap portion communicates with the outside of the adjustment portion through the opening.
[0019]
By forming the opening in the adjustment part in this way, the gap can be prevented from being completely covered. Therefore, even when the adjustment part is formed, the suction and discharge of the brake fluid is performed when the gap changes in size. Can be done.
[0020]
In the rotary pump according to the present invention, as shown in claim 8, the main pipe line (for transmitting the brake fluid pressure generated by the brake fluid pressure generating means (1 to 3) to the braking force generating means (4, 5) ( A) and an auxiliary pipe (D) for supplying brake fluid to the main pipeline side in order to increase the braking force generated by the braking force generation means, the suction port is connected to the brake fluid pressure through the auxiliary pipeline. The brake fluid on the generating means side can be sucked, and the discharge port is arranged so as to discharge the brake fluid toward the braking force generating means through the main pipeline.
[0021]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, embodiments shown in the drawings will be described.
[0022]
In FIG. 1, the brake piping schematic of the brake device which applied the trochoid pump as a rotary pump is shown. Hereinafter, the basic configuration of the brake device will be described with reference to FIG. In this example, in a front-wheel drive four-wheeled vehicle, an example in which the brake device according to the present invention is applied to a vehicle that constitutes a hydraulic circuit of X piping having piping systems of right front wheel-left rear wheel and left front wheel-right rear wheel. explain.
[0023]
As shown in FIG. 1, the brake pedal 1 is connected to a booster device 2, and the brake pedal force and the like are boosted by the booster device 2.
[0024]
The booster 2 includes a bush rod that transmits the boosted pedaling force to the master cylinder 3, and the bush cylinder presses the master piston disposed in the master cylinder 3. Pressure is generated. The brake pedal 1, the booster 2, and the master cylinder 3 correspond to brake fluid pressure generating means.
[0025]
The master cylinder 3 is connected to a master reservoir 3 a that supplies brake fluid into the master cylinder 3 and stores excess brake fluid in the master cylinder 3.
[0026]
The master cylinder pressure is transmitted to the wheel cylinder 4 for the right front wheel FR and the wheel cylinder 5 for the left rear wheel RL via an antilock brake device (hereinafter referred to as ABS). In the following description, the right front wheel FR and the left rear wheel RL side will be described. However, since the same applies to the left front wheel FL and the right rear wheel RR side which are the second piping system, the description will be omitted.
[0027]
The brake device is provided with a pipe line (main pipe line) A connected to the master cylinder 3, and the pipe line A is provided with a proportional control valve (PV: proportioning valve) 22. The proportional control valve 22 divides the pipe A into two parts. That is, the pipe A is divided into a pipe A1 that receives the master cylinder pressure between the master cylinder 3 and the proportional control valve 22, and a pipe A2 between the proportional control valve 22 and the wheel cylinders 4 and 5.
[0028]
The proportional control valve 22 normally has an action of transmitting the reference pressure of the brake fluid to the downstream side with a predetermined damping ratio when the brake fluid flows in the forward direction. Then, as shown in FIG. 1, by connecting the proportional control valve 22 in reverse, the pipe A2 side becomes the reference pressure.
[0029]
Further, in the pipeline A2, the pipeline A is branched into two, one of which is provided with a pressure increase control valve 30 for controlling the increase of the brake fluid pressure to the wheel cylinder 4, and the other is the wheel cylinder. A pressure increase control valve 31 for controlling the increase of the brake fluid pressure to 5 is provided.
[0030]
These pressure-increasing control valves 30 and 31 are configured as two-position valves that can control the communication / blocking state by an ABS electronic control unit (hereinafter referred to as ECU). When the two-position valve is controlled to be in communication, the master cylinder pressure or the brake fluid pressure generated by discharging the brake fluid from the pump can be applied to the wheel cylinders 4 and 5.
[0031]
Note that the first and second pressure-increasing control valves 30 and 31 are always controlled to communicate during normal braking when ABS control is not being executed. The pressure increase control valves 30 and 31 are provided with safety valves 30a and 31a, respectively, so that brake fluid is removed from the wheel cylinders 4 and 5 side when the brake depression is stopped and the ABS control is finished. It has become.
[0032]
Further, an ABS ECU is provided in a pipeline B connecting the pipeline A between the first and second pressure increase control valves 30, 31 and the wheel cylinders 4, 5 and the reservoir hole 20a of the reservoir 20. Depressurization control valves 32 and 33 that can control the communication / blocking state are respectively provided. These pressure reduction control valves 32 and 33 are always cut off in the normal brake state (when the ABS is not operating).
[0033]
A rotary pump 10 is disposed between safety valves 10a and 10b in a pipe C connecting the proportional control valve 22, the pressure increase control valves 30 and 31 of the pipe A, and the reservoir hole 20a of the reservoir 20. A motor 11 is connected to the rotary pump 10, and the rotary pump 10 is driven by the motor 11. A detailed description of the rotary pump 10 will be given later.
[0034]
In addition, a damper 12 is disposed on the discharge side of the rotary pump 10 in the pipe C in order to reduce the pulsation of the brake fluid discharged by the rotary pump 10. A pipe line (auxiliary pipe line) D is provided so as to connect between the reservoir 20 and the rotary pump 10 and the master cylinder 3, and the rotary pump 10 is connected to the pipe line via the pipe line D. The brake fluid of A1 is pumped up and discharged to the pipe A2, so that the wheel cylinder pressure in the wheel cylinders 4 and 5 is made higher than the master cylinder pressure to increase the wheel braking force. Note that the proportional control valve 22 maintains a differential pressure between the master cylinder pressure and the wheel cylinder pressure at this time.
[0035]
A control valve 34 is provided in the pipeline D, and the control valve 34 is always cut off during normal braking.
[0036]
In addition, a check valve 21 is disposed between the connection part of the pipe C and the pipe D and the reservoir 20 so as not to flow backward from the pipe C to the reservoir 20 due to the hydraulic pressure transmitted from the pipe D at this time. Has been.
[0037]
Note that the control valve 40 is a two-position valve that is normally in communication. When the master cylinder pressure is lower than a predetermined pressure, the control valve 40 is shut off when the wheel cylinders 4 and 5 are suddenly braked or TRC is cut off. The differential pressure between the side and the wheel cylinder side is maintained.
[0038]
Next, FIG. 2A shows a schematic view of the rotary pump 10, and FIG. 2B shows a cross-sectional view taken along the line AA of FIG. 2A. First, the structure of the rotary pump 10 will be described with reference to FIGS. 2 (a) and 2 (b).
[0039]
In the rotor chamber 50a of the casing 50 in the rotary pump 10, the outer rotor 51 and the inner rotor 52 are assembled and stored with their respective central axes (points X and Y in the figure) being eccentric. Yes. The outer rotor 51 includes an inner tooth portion 51a on the inner periphery, and the inner rotor 52 includes an outer tooth portion 52a on the outer periphery. The outer rotor 51 and the inner rotor 52 are meshed with each other by forming a plurality of gap portions 53 by the tooth portions 51a and 52a. As can be seen from FIG. 2A, the rotary pump 10 according to the present embodiment is a partition in which a gap portion 53 is formed by the inner tooth portion 51 a of the outer rotor 51 and the outer tooth portion 52 a of the inner rotor 52. It is a multi-tooth trochoid type pump without a plate (crescent). Further, in order to transmit the rotational torque of the inner rotor 52, the inner rotor 52 and the outer rotor 51 have a plurality of contact points.
[0040]
As shown in FIG. 2 (b), the casing 50 includes a first side plate portion 71 and a second side plate portion 72 arranged so as to sandwich both rotors 51 and 52 from both sides, and the first, A central plate portion 73 is provided between the second side plate portions 71 and 72 and provided with a hole for accommodating the outer rotor 51 and the inner rotor 52, thereby forming a rotor chamber 50a. .
[0041]
In addition, central holes 71a and 72a communicating with the inside of the rotor chamber 50a are formed in the central portions of the first and second side plates 71 and 72. The central holes 71a and 72a are arranged in the inner rotor 52. The provided drive shaft 54 is fitted. The outer rotor 51 and the inner rotor 52 are rotatably disposed in the hole of the central plate portion 73. In other words, the rotating portion composed of the outer rotor 51 and the inner rotor 52 is rotatably incorporated in the rotor chamber 50a of the casing 50, the outer rotor 51 rotates about the point X, and the inner rotor 52 sets the point Y. It will rotate as an axis.
[0042]
Furthermore, when a line passing through the point X and the point Y serving as the respective rotation axes of the outer rotor 51 and the inner rotor 52 is a center line Z of the rotary pump 10, the center line Z is sandwiched between the first side plate portions 71. On the left and right sides, a suction port 60 and a discharge port 61 communicating with the rotor chamber 50a are formed. The suction port 60 and the discharge port 61 are disposed at positions that communicate with the plurality of gaps 53. The brake fluid from the outside can be sucked into the gap 53 through the suction port 60 and the brake fluid in the gap 53 can be discharged to the outside through the discharge port 61.
[0043]
Among the plurality of gap portions 53, the closed portion 53a having the maximum volume and the closed portion 53b having the minimum volume are configured not to communicate with either the suction port 60 or the discharge port 61. The closed portions 53a and 53b hold the differential pressure between the suction pressure at the suction port 60 and the discharge pressure at the discharge port 61.
[0044]
The first side plate portion 71 is provided with a conduction path 73 a that connects the outer periphery of the outer rotor 51 and the suction port 60, and further, conduction paths 73 b and 73 c that communicate the outer periphery of the outer rotor 51 and the discharge port 61. Yes. The conduction path 73a is disposed at a position of about 90 degrees from the center line Z toward the suction port 60 with the point X serving as the rotation axis of the outer rotor 51 as the center. In addition, the conduction path 73b is formed so as to communicate the gap portion 53 closest to the confinement portion 53a and the outer periphery of the outer rotor 51 among the plurality of gap portions 53 communicating with the discharge port 61. The conduction path 73 c is formed so as to communicate the gap 53 closest to the confinement part 53 b and the outer periphery of the outer rotor 51 among the plurality of gaps 53 communicating with the discharge port 61. The conduction path 73b and the conduction path 73c are arranged at a position of about 22.5 degrees from the center line Z toward the discharge port 61 with the point X as the center.
[0045]
Further, the wall surface of the central plate 73 that forms the hole of the central plate 73 and at a position about 45 degrees from the center line Z toward the suction port 60 with the point X serving as the rotation axis of the outer rotor 51 as the center. A recess 73d and a recess 73e are formed, and seal members 80 and 81 for suppressing the flow of brake fluid on the outer periphery of the outer rotor 51 are provided in the recesses 73 and 73e. Specifically, the seal members 80 and 81 are disposed between the conduction path 71b and the conduction path 71d, and seal the portion where the brake hydraulic pressure is low and the portion where the brake hydraulic pressure is high on the outer periphery of the outer rotor 51. It is supposed to be.
[0046]
The seal member 80 includes a substantially cylindrical rubber member 80a and a rectangular parallelepiped Teflon resin member 80b. The resin member 80 b is pressed by the rubber member 80 a and comes into contact with the outer rotor 51. That is, a slight error is generated in the size of the outer rotor 51 due to a manufacturing error or the like, and this error can be absorbed by the rubber member 80a having an elastic force.
[0047]
The width of the resin member 80b is such that there is a certain gap when the resin member 80b is disposed in the recess 73d. In other words, if the width of the resin member 80b is formed to be equal to the width of the recess 73d, the resin member 80b becomes difficult to come out when entering the recess 73d due to the flow of the brake fluid pressure when the pump is driven, so that there is a slight gap. By forming the resin member 80b with a certain size, the brake fluid enters the upper portion of the resin member 80b, and the pressure of the brake fluid makes it easy for the resin member 80b to come out of the recess 73d. Note that the configuration of the seal member 81 is the same as that of the seal member 80, and thus the description thereof is omitted.
[0048]
Further, as shown in FIG. 2B, groove portions 71 b and 72 b are formed in the first and second side plate portions 71 and 72. As shown by the two-dot chain line in FIG. 2A, the groove portions 71b and 72b are formed in an annular shape surrounding the drive shaft 54, and the groove width is widened in a predetermined region. . Specifically, the centers of the grooves 71 b and 72 b are in a state of being eccentric to the suction port 60 side (the left side of the drawing) with respect to the shaft center of the drive shaft 54.
[0049]
Accordingly, the grooves 71 b and 72 b pass between the discharge port 61 and the drive shaft 54 and are disposed so as to pass through the portions where the closing portions 53 a and 53 b and the seal members 80 and 81 seal the outer rotor 51. It becomes.
[0050]
Assuming a line connecting the shaft of the drive shaft 54 and the centers of the grooves 71b and 72b, the grooves 71b and 72b are formed at the position where the line intersects the suction port 60 or the discharge port 61 with the inner rotor 51 and the outer rotor. The groove width is increased so as to overlap both of the two. In addition, the groove widths of the groove portions 71b and 72b are also increased at the portions overlapping the closed portions 53a and 53b.
[0051]
Seal members 100 and 101 having shapes similar to the shapes of the groove portions 71b and 72b are disposed in the groove portions 71b and 72b having such a configuration, respectively. A schematic diagram of these seal members 100 and 101 is shown in FIG. As shown in FIG. 3, the seal members 100 and 101 are configured such that a predetermined region of an annular member is formed wide.
[0052]
The wide portions 100A and 101A formed to be wide are configured to overlap the outer rotor 51 and the inner rotor 52 at the positions where the discharge ports 61 are formed, and the suction ports 60 are formed in the wide portions 100B and 101B. In this position, the outer rotor 51 and the inner rotor 52 are overlapped with each other. The wide portions 100A and 101A and the wide portions 100B and 101B play a role of suppressing axial displacement between the outer rotor 51 and the inner rotor 52. Note that the regions where the wide portions 100A and 101A and the wide portions 100B and 101B are disposed, that is, the regions where the discharge ports 61 and the suction ports 60 are formed are regions that do not need to be sealed, and these wide portions 100A. , 101A and the wide portions 100B, 101B are disposed only for the purpose of suppressing the axial displacement of the outer rotor 51 and the inner rotor 52.
[0053]
Further, the wide portions 100C and 101C and the wide portions 100D and 101D are configured to have a width so as to completely cover the closed portion 53a and the closed portion 53b, respectively. The brakes in the closed portions 53a and 53b are mainly used. Serves as a seal to prevent liquid leakage. The wide portions 100C and 101C and the wide portions 100D and 101D also serve to eliminate axial displacement of the outer rotor 51 and the inner rotor 52, but the wide portions 100A and 101A and the wide portions 100B and 101B play the role. Therefore, it is not necessary to press the outer rotor 51 and the inner rotor 52 with the wide portions 100C and 101C and the wide portions 100D and 101D in order to prevent deviation.
[0054]
These seal members 100 and 101 are constituted by elastic members 100a and 101a made of an elastic body such as rubber, and resin members 100b and 101b made of resin. The resin members 100b and 101b are arranged so as to be in contact with the inner rotor 52, the outer rotor 51 and the central plate 73, and are pressed by the elastic members 100a and 101a arranged on the bottom side of the grooves 71b and 72b with respect to the resin members 100b and 101b. And configured to perform a sealing function.
[0055]
In the gap between the axial end surfaces of the inner rotor 52 and the outer rotor 51 and the first and second side plate portions 71, 72 by the seal members 100, 101 arranged in this way, the high-pressure discharge port 61, The gap between the low-pressure drive shaft 54 and the inner rotor 52 and the suction port 60 can be sealed.
[0056]
In order to seal the high pressure portion and the low pressure portion in the gap between the axial end surfaces of the inner rotor 52 and the outer rotor 51 and the first and second side plate portions 71 and 72, the sealing member 100 is used. , 101 needs to pass between the discharge port 61 and the drive shaft 54 and between the discharge port 61 and the suction port 60 and reach the outer periphery of the outer rotor 51. On the other hand, in the present embodiment, of the seal members 100 and 101, the region from the seal member 80 through the drive shaft 54 and the discharge port 61 to the seal member 81 is a high-pressure portion. In other regions where sealing is not required, the portions contacting the inner rotor 52 and the outer rotor 51 are negligibly small. For this reason, the contact resistance by the sealing members 100 and 101 can be reduced, and the mechanical loss can be reduced.
[0057]
Furthermore, as described above, the wide portions 100A and 101A and the wide portions 100B and 101B can eliminate the axial displacement of the outer rotor 51 and the inner rotor 52. In this way, the wide portions 100A and 101A and the wide portions 100B and 101B that do not need to play a role as seals serve to eliminate the axial displacement of the outer rotor 51 and the inner rotor 52. The wear of the wide portions 100C and 101C and the wide portions 100D and 101D can be reduced. Thereby, the fall of the sealing function of wide part 100C, 101C and wide part 100D, 101D can be suppressed.
[0058]
The wide portions 100A and 101A and the wide portions 100B and 101B are formed with openings so that the wide portions 100A and 101A and the wide portions 100B and 101B do not cover all of the plurality of gaps 53. It has become. This is because the gap portion 53 sucks and discharges the brake fluid by changing in size, and therefore it is preferable that the gap portion 53 is connected to the suction port 60 or the discharge port 61. The brake fluid can be sucked and discharged in the portion 53.
[0059]
Next, the operation of the brake device and the rotary pump 10 configured as described above will be described.
[0060]
The control valve 34 provided in the brake device is appropriately connected when a large braking force is required, for example, when a braking force corresponding to the brake depression force cannot be obtained or when the operation amount of the brake pedal 1 is large. The The high pressure master cylinder pressure generated by the depression of the brake pedal 1 through the pipe D is applied to the rotary pump 10.
[0061]
On the other hand, in the rotary pump 10, the inner rotor 52 rotates in accordance with the rotation of the drive shaft 54 by driving the motor 11, and the outer rotor 51 also moves in the same direction due to the meshing of the inner tooth portion 51a and the outer tooth portion 52a. Rotate to. At this time, since the volume of each gap portion 53 changes in size while the outer rotor 51 and the inner rotor 52 make one rotation, the brake fluid is sucked from the suction port 60 and is directed from the discharge port 61 toward the pipeline A2. Exhale brake fluid. The wheel cylinder pressure is increased by the discharged brake fluid.
[0062]
As described above, the rotary pump 10 can perform a basic pumping operation in which the brake fluid is sucked from the suction port 60 and the brake fluid is discharged from the discharge port 61 when the rotors 51 and 52 are rotated.
[0063]
During the pump operation, the suction port 60 side of the outer periphery of the outer rotor 51 is set to suction pressure by the brake fluid sucked through the conduction path 73a, and the discharge port 61 side of the outer periphery of the outer rotor 51 is connected to the conduction paths 73b and 73c. The discharge pressure is set by the brake fluid sucked through. For this reason, a low pressure portion and a high pressure portion are generated on the outer periphery of the outer rotor 51. Even in the gaps between the axial end surfaces of the inner rotor 52 and the outer rotor 51 and the first and second side plate portions 71, 72, the low-pressure discharge port 60 and the drive shaft 54 are connected to the inner rotor 52. The low pressure portion and the high pressure portion are generated by the gap and the high pressure discharge port 61.
[0064]
However, as described above, since the low pressure portion and the high pressure portion of the outer periphery of the outer rotor 51 are sealed and separated by the seal members 80 and 81, the high pressure portion on the discharge port 61 side through the outer periphery of the outer rotor 51. Oil leakage does not occur toward the low pressure portion on the suction port 50 side. Further, the low pressure portion and the high pressure portion of the gap between the axial end surfaces of the inner rotor 52 and the outer rotor 51 and the first and second side plate portions 71 and 72 are sealed by the seal members 100 and 101. Therefore, oil leakage does not occur from the high pressure part to the low pressure part. In FIG. 2, the seal members 100 and 101 are illustrated so as not to contact the outer rotor 51 and the inner rotor 52, but the seal members 100 and 101 bend as the discharge port 61 becomes high pressure, and the outer rotor 51 and the inner rotor 51 Fully contacts the rotor 52 and performs a sealing function.
[0065]
Further, since the axial displacements of the outer rotor 51 and the inner rotor 52 are aligned by the wide portions 100A and 101A and the wide portions 100B and 101B, good pump performance can be obtained. The wide portions 100A, 101A and the wide portions 100B, 101B, which do not need a role as seals, can eliminate the axial displacement of the outer rotor 51 and the inner rotor 52, so that the wide portions 100C that cover the closed portions 53a, 53b, Wear of 101C and the wide portions 100D and 101D can be reduced.
[0066]
Since the seal members 100 and 101 are formed so as to pass through the seal members 80 and 81, there is no gap between the seal members 100 and 101 and the seal members 80 and 81. Will not occur.
[0067]
Further, due to the seal members 80, 81, the suction port 60 side of the outer periphery of the outer rotor 51 becomes a low pressure, and the pressure is the same as that of the gap portion 53 communicating with the suction port 60. The discharge port 61 side has a high pressure, which is the same pressure as the gap portion 53 communicating with the discharge port 61. For this reason, the pressure balance inside and outside of the outer rotor 51 is maintained, and the pump can be driven stably.
[0068]
As described above, the outer rotor 51 and the wide portions 100A and 101A and the wide portions 100B and 101B which do not need to play the sealing function as well as the wide portions 100C and 101C and the wide portions 100D and 101D which play the sealing function. By eliminating the axial displacement of the inner rotor 52, the durability of the wide portions 100C, 101C and the wide portions 100D, 101D as seals can be improved.
[0069]
(Second Embodiment)
In the present embodiment, the configuration of the seal members 100 and 101 is changed with respect to the first embodiment. FIG. 4 shows an enlarged cross-sectional view of the seal member 100 in the present embodiment. Note that the sealing member 101 is omitted because it has the same configuration as the sealing member 100.
[0070]
In the present embodiment, as shown in FIG. 4, the size of the elastic member 100a is reduced with respect to the seal member 100 (see FIG. 2) in the first embodiment, and a resin member is provided on the inner peripheral side of the elastic member 100a. 100c is arranged.
[0071]
Thereby, the area where the resin member 100b is pressed by the elastic member 100a can be made small. For this reason, the area | region where the resin member 100b presses the inner rotor 52 and the outer rotor 51 decreases, the contact resistance by the sealing member 100 can be made small, and a mechanical loss can be reduced more.
[0072]
The interval S1 between the resin member 100c and the resin member 100a is narrower than the interval S2 between the first and second side plates 71 and 72 and the outer rotor 51 or the inner rotor 52.
[0073]
By the way, the outer rotor 51 and the inner rotor 52 may both move in the axial direction due to the manufacturing intersection of the elastic members 100a and 101a and the resin members 100b and 101b and the axial force applied to the outer rotor 51 and the inner rotor 52. .
[0074]
In such a case, since the elastic members 100a and 101a expand and contract, the axial movement of the outer rotor 51 and the inner rotor 52 cannot be completely suppressed, and both the outer rotor 51 and the inner rotor 52 move in the axial direction, It may occur that the first and second side plates 71 and 72 come into contact with each other and a large contact resistance is generated.
[0075]
For this reason, in the present embodiment, the resin members 100c and 101c regulate the resin members 100b and 101b so that the resin members 100b and 101b cannot move more than the distance S1 between the first and second side plates 71 and 72 and the outer rotor 51 or the inner rotor 52. This prevents the outer rotor 51 and the inner rotor 52 from coming into contact with the first and second side plates 71 and 72. Thereby, it is possible to prevent the contact resistance due to the outer rotor 51 and the inner rotor 52 coming into contact with the first and second side plates 71 and 72 from being increased, and to reduce the mechanical loss.
[0076]
Note that the contact resistance of the sealing member 101 having the same configuration can be reduced. Thereby, mechanical loss can be reduced more.
[0077]
In this embodiment, the resin member 100c is configured as a single member. However, the resin member 100c may be configured integrally with the resin member 100b, or may be configured integrally with the first and second side plate portions 71 and 72. May be.
[0078]
(Third embodiment)
In contrast to the first and second embodiments, the configuration of the seal members 100 and 101 may be changed as in the present embodiment.
[0079]
In the first and second embodiments, the wide portions 100 </ b> A and 101 </ b> A have a width that can reach only the inner side of the outer periphery of the outer rotor 51, but the width may be further increased to reach the center plate 73. In this way, since the seal members 100 and 101 are constructed by the central plate 73, the deflection of the seal members 100 and 101 can be reduced.
[0080]
(Other embodiments)
In the second embodiment, it is shown that the pressing force by the elastic members 100a and 101a is reduced by the resin members 100c and 101c. However, by adjusting the shapes of the resin members 100c and 101c and the elastic members 100a and 101a, It is also possible to adjust the position to be sealed. In other words, at the position where the elastic members 100a and 101a are arranged, the brake fluid pressure strongly presses the resin members 100c and 101c to perform sealing, so that it matches the shape of the adjusted elastic members 100a and 101a. By adjusting the shape of the resin members 100c and 101c, it is possible to adjust the position to be strongly sealed.
[0081]
Here, consider the brake fluid pressure inside the confinement portion 53a. The gap 53 moves from the suction port 60 side and becomes a closed portion 53a. At this time, the brake fluid pressure inside the confinement part 53a is low. Thereafter, when the gap 53 further moves, the gap 53 communicates with the discharge port 61, so that the brake fluid inside the gap 53 instantaneously increases in pressure.
[0082]
For this reason, with respect to the closing portion 53a, the elastic member 100a, 101a may be disposed so that the position at the moment when it becomes the high pressure side is distinguished from the high pressure side and the low pressure side so as to pass through the position. .
[0083]
However, since a change in the rotational behavior of the rotary pump 10 and a manufacturing intersection occur, it is not always easy to distinguish between the high pressure side and the low pressure side of the confining portion 53a. For this reason, an average value of the brake fluid pressure during rotation of the rotary pump 10 may be obtained, and an optimum position may be sealed based on the average value. For example, the position where the average value matches the intermediate value between the high pressure and the low pressure may be sealed.
[0084]
Note that the wide portions 100A and 101A and the wide portions 100B and 101B are not limited to the positions in the above-described embodiment, but may be formed at other positions as long as they do not require a role as a seal.
[0085]
Further, as shown in FIG. 5, the seal member 100 may be disposed only on one side of the first side plate 71. At this time, due to the elasticity of the O-ring 100a of the seal member 100, the seal member 80b is pushed by the resin member 100b so that the seal member 100b comes into contact with the inner rotor 52 and the outer rotor 51, whereby the inner rotor 52 and the outer rotor 51 are pressed. Is moved to the second side plate 72 side, the gap between the inner rotor 52 and the outer rotor 51 and the second side plate 72 is reduced as much as possible. Accordingly, even in the second side plate 72 on the side where the seal member 100 does not exist, the gap between the inner rotor 52 and the outer rotor 51 and the second side plate 72 is about several microns, and the above-described embodiment (for example, 2), the sealing member 101 has substantially the same sealing performance as the case where the sealing member 101 exists, and the axial displacement between the inner rotor 52 and the outer rotor 51 is substantially eliminated.
[Brief description of the drawings]
FIG. 1 is a pipe configuration diagram of a brake device including a rotary pump according to an embodiment of the present invention.
2 is a diagram showing a specific configuration of the rotary pump in FIG. 1. FIG.
FIG. 3 is a schematic view of a seal member 100 (101) shown in FIG.
FIG. 4 is an enlarged view of a seal member in the second embodiment.
FIG. 5 is a diagram showing a cross-sectional configuration of a rotary pump according to another embodiment.
FIG. 6 is a diagram for explaining a configuration of a rotary pump studied by the present inventors.
[Explanation of symbols]
51 ... Outer rotor, 51a ... Internal tooth part, 52 ... Inner rotor,
52a ... external tooth part, 53 ... gap part, 53a, 53b ... confinement part,
54 ... Drive shaft, 60 ... Suction port, 61 ... Discharge port, 71 ... First side plate,
72 ... second side plate, 71a, 72a ... center hole,
71b, 72b ... groove, 73 ... center plate,
73a, 73b, 73c ... communication passage, 80, 81 ... sealing member,
100, 101 ... sealing member, 100a, 101a ... elastic member,
100b, 101b ... resin member, 100c, 101c ... resin member.
100A, 101A ... wide portion, 100B, 101B ... wide portion.

Claims (8)

  1. An outer rotor (51) having an inner tooth portion (51a) on an inner periphery, and an inner rotor (52) having an outer tooth portion (52a) and rotating around a drive shaft (54), the inner teeth a rotation unit which is constructed with pairs seen to form a plurality of gap portions (53) by engaging a part and the outer teeth,
    Having openings (71a, 72a) into which the drive shaft is fitted, and having a suction port (60) for sucking fluid into the rotating part and a discharge port (61) for discharging the fluid from the rotating part, A casing (50) covering the rotating part;
    Among the plurality of gaps, the pressure difference between the suction port and the discharge port at the first confinement portion (53a) having the maximum volume and the second confinement portion (53b) having the minimum volume. In the rotary pump that sucks the fluid from the suction port by the rotational movement of the rotating part and discharges the fluid through the discharge port,
    In the gap between the axial end surfaces of the inner rotor and the outer rotor and the casing, it passes between the discharge port and the drive shaft and passes through the first and second confinement portions. An adjustment portion (100A) that matches the positions of the inner rotor and the outer rotor in the axial direction of the drive shaft at a portion that reaches the outer periphery of the outer rotor and is different from a portion that passes through the first and second confinement portions. , 101A, 100B, 101B) with sealing means (100, 101),
    In the sealing means, the outer periphery of the outer rotor located on the discharge port side and the gap portion communicating with the discharge port communicate with each other through the gap portion, and the suction shaft is connected between the drive shaft and the inner rotor. A rotary pump characterized in that it is configured to communicate with the gap that communicates with the mouth.
  2. The casing is
    A central plate (73) having a hole for accommodating the rotating part;
    The first and second side plates (71, 72) having holes (71a, 72a) into which the drive shafts are inserted and sandwiching the central plate;
    The first and second side plates pass between the discharge port and the drive shaft, pass through the first and second confinement portions, reach the outer periphery of the outer rotor, and 1. Groove portions (71b, 72b) extending from the inner rotor to the outer rotor or the central plate are formed in a portion different from the portion that passes through the second confinement portion, and the groove portions are formed in the groove portions. 2. The rotary pump according to claim 1, wherein the sealing means is disposed.
  3. The sealing means includes
    A first seal member (100a, 101a) made of an elastic body and disposed on the bottom side of the groove portion, and a second seal member disposed on the opening side of the groove portion with respect to the first seal member And a seal member (100b, 101b), wherein the second seal member is in contact with the inner rotor and the outer rotor by the elastic force of the first seal member. The rotary pump according to claim 2.
  4. The rotation according to any one of claims 1 to 3, wherein the adjustment portion is extended so as to overlap the gap portion communicating with the discharge port or the suction port. Type pump.
  5. The seal member has an annular portion having a substantially annular shape, and the annular portion is arranged eccentric with respect to the drive shaft,
    The adjustment part is configured by partially widening the annular part so as to overlap with the gap part communicating with the discharge port or the suction port. Item 4. The rotary pump according to any one of Items 1 to 3.
  6. The rotary pump according to any one of claims 1 to 5, wherein a plurality of the adjusting portions are formed and arranged at symmetrical positions with the drive shaft as a center.
  7. The adjustment portion has an opening formed therein, and the gap portion communicates with the outside of the adjustment portion through the opening. The rotary pump described in 1.
  8. Brake fluid pressure generating means (1-3) for generating brake fluid pressure based on the pedal effort;
    Braking force generating means (4, 5) for generating a braking force on the wheel based on the brake fluid pressure;
    A main line (A) connected to the brake fluid pressure generating means and transmitting the brake fluid pressure to the braking force generating means;
    A brake device connected to the brake fluid pressure generating means and having an auxiliary pipeline for supplying brake fluid to the main pipeline side in order to increase the braking force generated by the braking force generating means;
    The rotary pump according to any one of claims 1 to 7, wherein the suction port can suck the brake fluid on the brake fluid pressure generating means side through the auxiliary conduit, and the discharge port is connected to the braking force generating means through the main conduit. A brake device comprising a rotary pump, wherein the brake device is arranged so that the brake fluid can be discharged toward the vehicle.
JP28477899A 1998-10-06 1999-10-05 Rotary pump and brake device equipped with rotary pump Expired - Fee Related JP4221843B2 (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
JP28422898 1998-10-06
JP10-284228 1998-10-06
JP28477899A JP4221843B2 (en) 1998-10-06 1999-10-05 Rotary pump and brake device equipped with rotary pump

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP28477899A JP4221843B2 (en) 1998-10-06 1999-10-05 Rotary pump and brake device equipped with rotary pump

Publications (2)

Publication Number Publication Date
JP2000179466A JP2000179466A (en) 2000-06-27
JP4221843B2 true JP4221843B2 (en) 2009-02-12

Family

ID=26555378

Family Applications (1)

Application Number Title Priority Date Filing Date
JP28477899A Expired - Fee Related JP4221843B2 (en) 1998-10-06 1999-10-05 Rotary pump and brake device equipped with rotary pump

Country Status (1)

Country Link
JP (1) JP4221843B2 (en)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10262395B4 (en) * 2001-08-09 2016-03-03 Denso Corporation Rotary pump with higher delivery pressure and brake device having the same
JP2007263116A (en) * 2001-08-09 2007-10-11 Denso Corp Rotary pump and brake apparatus having the same
JP4007080B2 (en) * 2002-06-06 2007-11-14 株式会社アドヴィックス Rotary pump for brake equipment

Also Published As

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