JP4617617B2 - Plunger type pump device - Google Patents

Plunger type pump device Download PDF

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Publication number
JP4617617B2
JP4617617B2 JP2001217536A JP2001217536A JP4617617B2 JP 4617617 B2 JP4617617 B2 JP 4617617B2 JP 2001217536 A JP2001217536 A JP 2001217536A JP 2001217536 A JP2001217536 A JP 2001217536A JP 4617617 B2 JP4617617 B2 JP 4617617B2
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Japan
Prior art keywords
fluid
piston
plunger
sub
means
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Expired - Fee Related
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JP2001217536A
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Japanese (ja)
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JP2003028077A (en
Inventor
明徳 奥谷
明宏 横山
康仁 関原
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株式会社アドヴィックス
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    • BPERFORMING OPERATIONS; TRANSPORTING
    • B60VEHICLES IN GENERAL
    • B60TVEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T8/00Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
    • B60T8/32Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
    • B60T8/34Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
    • B60T8/36Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition including a pilot valve responding to an electromagnetic force
    • B60T8/3615Electromagnetic valves specially adapted for anti-lock brake and traction control systems
    • B60T8/3675Electromagnetic valves specially adapted for anti-lock brake and traction control systems integrated in modulator units
    • B60T8/368Electromagnetic valves specially adapted for anti-lock brake and traction control systems integrated in modulator units combined with other mechanical components, e.g. pump units, master cylinders
    • BPERFORMING OPERATIONS; TRANSPORTING
    • B60VEHICLES IN GENERAL
    • B60TVEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T8/00Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
    • B60T8/32Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
    • B60T8/34Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
    • B60T8/40Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition comprising an additional fluid circuit including fluid pressurising means for modifying the pressure of the braking fluid, e.g. including wheel driven pumps for detecting a speed condition, or pumps which are controlled by means independent of the braking system
    • B60T8/4031Pump units characterised by their construction or mounting
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404Details or component parts
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B11/00Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation
    • F04B11/0008Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using accumulators
    • F04B11/0033Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using accumulators with a mechanical spring
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/22Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
    • F04B49/24Bypassing
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/001Noise damping

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a plunger-type pump device, and more particularly to a plunger-type pump device suitable for a vehicle brake fluid pressure control device and the like.
[0002]
[Prior art]
Modern vehicles are equipped with devices that perform various controls such as anti-skid control, traction control, front / rear braking force distribution control, etc., and a hydraulic pump that provides these controls is equipped with a plunger pump It has been. For example, JP-A-8-40234 discloses a plunger type pump for use in a vehicle hydraulic brake device. This publication relates to a so-called vacuum filling method in which when a brake fluid is filled in a hydraulic brake device, the brake fluid is supplied after the air is released from a master cylinder reservoir, the brake fluid is supplied to a pump chamber (compression chamber) of a plunger pump. As a means for solving this problem, it has been proposed to form a vacuum transmission slit in the seat portion of the discharge valve. It is described that the vacuum transmission slit may be formed in the seat portion of the suction valve.
[0003]
[Problems to be solved by the invention]
By the way, in the conventional plunger type pump as described in the above publication, since noise is generated particularly in the discharge mode of the pump, it is required to reduce this. FIGS. 28 to 30 show the operating state of a general plunger type pump and explain the state of noise generation. The pump is composed of a suction check valve (suction valve) IV and a discharge check valve (discharge valve). OV), and these are usually constituted by a spherical valve body and a spring for biasing it. The plunger PR is reciprocated by a drive device having a drive cam DR driven by an electric motor (not shown), whereby the compression chamber CP is contracted and expanded. The discharge side of the pump is connected to the damper chamber DP, and the suction side of the pump is connected to a normally closed electromagnetic valve NC that constitutes an actuator of a hydraulic brake device as described in the above publication and a low pressure reservoir RS. . As will be described later, the generation of noise becomes a problem particularly when the suction side of the pump is in a closed space. Therefore, in FIGS. 28 to 30, the solenoid valve NC is in the closed position and the low-pressure reservoir RS is fluid. It shows an empty state without (brake fluid).
[0004]
FIG. 28 shows a state in which the pump discharge mode ends (top dead center of the plunger PR). At this time, the suction valve IV is in the closed position and the compression chamber CP is reduced to the minimum capacity Q. OV is an open position, and a gap is formed between the spherical valve body and the seat portion. Thus, the brake fluid in the compression chamber CP is discharged into the damper chamber DP from the gap of the discharge valve OV. Next, when the drive cam DR rotates as indicated by an arrow and shifts from the top dead center to the bottom dead center, the compression valve CP is expanded while the suction valve IV remains in the closed position. Therefore, if the discharge valve OV is immediately closed at this stage, the pressure in the compression chamber CP is only reduced while the amount of brake fluid in the compression chamber CP remains at the minimum capacity Q. It takes time until the spherical valve element is seated on the seat portion, and the brake fluid of ΔQ1 flows from the damper chamber DP into the compression chamber CP. Therefore, the amount of brake fluid in the compression chamber CP in FIG. 29 increases to (Q + ΔQ1).
[0005]
Then, when the drive cam DR further rotates as shown by the arrow from the state of FIG. 29 and reaches the top dead center as shown in FIG. 30, the brake fluid (Q + ΔQ1) in the compression chamber CP is compressed. At this time, since the discharge valve OV is in the closed position, the pressure in the compression chamber CP rises to a pressure slightly exceeding the pressure Pd in the damper chamber DP as shown by a thin two-dot chain line at the point (c) in FIG. To do. This increased pressure is transmitted to the drive cam DR via the plunger PR, and noise is generated in a motor portion (not shown). In addition, the (a) point of FIG. 31 and the (b) point have shown the pressure in the compression chamber CP in the state of FIG.28 and FIG.29, respectively.
[0006]
In this case, for example, when a vacuum transmission slit is formed in the seat portion of the suction valve, as in the pump described in the above-mentioned publication, the brake fluid in the compression chamber CP is passed through the slit. It can be estimated that an amount of ΔQ2 (substantially equal to ΔQ1) can flow out, but since the suction side is a closed hydraulic pressure path as described above, the pressure in the compression chamber CP is equal to the pressure in the damper chamber DP. It rises until it becomes almost equal. Further, as shown in FIG. 28, the plunger PR is provided with a resin seal member SL, and this seal member SL does not constitute a complete seal. However, since the suction side is a closed hydraulic pressure path as in the case of the slit, the pressure in the compression chamber CP cannot be reduced. Further, since this gap varies, it is not possible to use the seal member SL as a communication hole as it is for noise countermeasures without special setting.
[0007]
Accordingly, an object of the present invention is to reduce noise caused by the operation of a discharge valve, in particular, with a simple configuration in a plunger-type pump device. In the present invention, the plunger type pump device in which a low pressure reservoir is connected to the suction side of the plunger type pump is an object, and the application target is not limited to the vehicle hydraulic brake device, and can be widely applied to fluid devices. is there.
[0008]
[Means for Solving the Problems]
In order to solve the above problems, a plunger-type pump device according to the present invention includes a housing that forms a compression chamber, and a plunger that is slidably accommodated in the housing and disposed so that one end is exposed in the compression chamber. A drive means for reciprocatingly driving the plunger, a discharge valve communicating with the compression chamber, a suction valve communicating with the compression chamber, a fluid having a predetermined pressure or more, and at least via the suction valve In the plunger type pump device having a low pressure reservoir connected to the compression chamber, an outflow permitting means for allowing a small amount of fluid to flow out from the compression chamber to the low pressure reservoir side even when the suction valve is in a closed position. And a capacity space that can accommodate a minute amount of fluid that has flowed out of the outflow permission means, and that accommodates the fluid under a minute pressure smaller than the predetermined pressure. That.
[0009]
In the plunger type pump device, as described in claim 2, the intake valve includes a valve seat and a valve body biased to be seated on the valve seat, and the valve body and the valve seat It is preferable that at least one of the slits is formed and the outflow permission means is constituted by the slit. Thus, the outflow permitting means allows a small amount of fluid to flow out from the compression chamber to the low pressure reservoir side through the slit even when the suction valve is in the closed position.
[0010]
According to a third aspect of the present invention, the plunger is slidably accommodated in the housing via a seal member that allows a small amount of fluid to pass from the compression chamber, and the outflow is performed by the seal member. It is good also as comprising an allowance means.
[0011]
The low-pressure reservoir, as described in claim 4, is at least a cylinder communicating with the compression chamber via the suction valve, and is slidably accommodated in the cylinder, and fluid is accommodated in the cylinder. It is preferable to include a piston that forms a fluid chamber, and an urging means that urges the piston in a direction to reduce the fluid chamber.
[0012]
5. The apparatus according to claim 4, wherein, as described in claim 5, a recess is formed on a surface of the piston exposed to the fluid chamber, and the recess is covered with a diaphragm member, and the diaphragm member is The capacity space of the capacity means may be constituted by an enlarged space formed in the fluid chamber when deformed inside the recess. Further, as described in claim 6, the diaphragm member may be formed integrally with the piston.
[0013]
In the apparatus according to claim 4, as described in claim 7, an annular groove is formed on an outer periphery of the piston, and a predetermined gap is formed in the sliding direction of the piston with respect to the annular groove. A capacity space of the capacity means may be configured by an enlarged space formed between the annular elastic member and the annular groove when the annular elastic member is deformed and the annular elastic member is deformed. .
[0014]
5. The apparatus according to claim 4, further comprising reverse biasing means for biasing the piston in a direction opposite to the biasing direction of the biasing means as in claim 8. The fluid chamber may be enlarged by adjusting a relative urging force of the urging means with respect to the urging means, and the capacity space of the capacity means may be configured by the enlarged space.
[0015]
In the apparatus according to claim 8, the reverse biasing means may be an elastic member interposed between the piston and the cylinder as described in claim 9. Examples of the elastic member include a disc spring, a coil spring, and an elastic resin ring.
[0016]
2. The apparatus according to claim 1, wherein the capacity means includes a sub-cylinder formed on the piston so as to communicate with the fluid chamber, and is slidably received in the sub-cylinder. The sub-cylinder may include a sub-piston that forms a sub-fluid chamber that accommodates fluid in the sub-cylinder, and a sub-bias unit that urges the sub-piston in a direction to reduce the sub-fluid chamber. .
[0017]
Alternatively, as defined in claim 11, the capacity means is slidably accommodated in the sub-cylinder and a sub-cylinder formed in the housing so as to communicate with the fluid chamber. A sub-piston that forms a sub-fluid chamber that contains fluid, and sub-bias means that urges the sub-piston in a direction to reduce the sub-fluid chamber may be provided.
[0018]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, preferred embodiments of the present invention will be described with reference to the drawings. FIG. 1 shows an embodiment of a plunger type pump device according to the present invention. A housing 1 is formed with a damper chamber DP and a compression chamber CP, and holes 1a and 1b communicating with the compression chamber CP are formed. Has been. In this hole 1a, the plunger 2 is slidably accommodated, and is arranged so that one end is exposed to the compression chamber CP.
[0019]
The plunger 2 of the present embodiment has a spool shape, and an annular seal member S1 is fitted in the central annular groove 2a, so that the front and rear of the plunger 2 can be slid in the hole 1a in a state of being fluidly blocked. It is configured. A driving cam 4 that is driven to rotate by an electric motor (not shown) is disposed around a shaft 3 that is orthogonal to the axis of the hole 1a as a driving means for reciprocatingly driving the plunger 2. And the plunger 2 is urged | biased by the coil spring 5 stretched between the sheet | seat member 6a mentioned later and the plunger 2 so that the outer peripheral cam surface of the drive cam 4 may be pressed. The end face of the plunger 2 that contacts the drive cam 4 is at atmospheric pressure. Thus, since the drive cam 4 is driven to rotate about the shaft 3 that is in a positional relationship eccentric with respect to the center thereof, the plunger 2 that contacts the outer peripheral cam surface of the drive cam 4 reciprocates in the hole 1a. . In the present embodiment, the plunger 2 is set to reciprocate once by one rotation of the drive cam 4.
[0020]
In addition, a discharge valve 6 is connected to the compression chamber CP, and a suction valve 7 is connected to the compression chamber CP through a hole 1b. The discharge valve 6 of this embodiment constitutes a check valve, and a spherical valve seated on a seat member 6a fitted in the compression chamber CP and a valve seat around the discharge hole 6e formed in the seat member 6a. It comprises a body 6b, a coil spring 6c that urges the spherical valve body 6b in the seating direction, and a retainer 6d that is locked to the seat member 6a so as to hold the coil spring 6c. Similarly, the suction valve 7 of the present embodiment also constitutes a check valve, and includes a seat member 7a fitted in a hole 1b communicating with the compression chamber CP, and a periphery of the suction hole 7e formed in the seat member 7a. A spherical valve body 7b seated on the valve seat, a coil spring 7c for urging the spherical valve body 7b in the seating direction, and a retainer 7d engaged with the seat member 7a so as to hold the coil spring 7c. .
[0021]
A minute slit 7s is formed in a valve seat around the suction hole 7e on which the spherical valve body 7b is seated of the seat member 7a. Accordingly, even when the spherical valve body 7b is seated on the valve seat around the suction hole 7e and the suction valve 7 is in the closed position, a small amount of fluid is allowed to flow out from the compression chamber CP to the low pressure reservoir 10 side. . Thus, in the present embodiment, the outflow permitting means of the present invention is constituted by the slit 7s.
[0022]
A low pressure reservoir 10 is connected to the suction valve 7, and the low pressure reservoir 10 can be connected to the compression chamber CP via the suction valve 7. The low-pressure reservoir 10 of the present embodiment has a configuration similar to that shown in FIGS. 4 and 5 and can contain a fluid having a predetermined pressure or higher. That is, the piston 11 is slidably accommodated in the cylinder 10a connected to the compression chamber CP through the suction valve 7 at least, and a fluid chamber is provided between the top surface of the piston 11 and the inner wall of the cylinder 10a. CF is formed. A seal member S2 is disposed on the outer periphery of the piston 11, and the fluid chamber CF and the inside of the cylinder 10a on the opposite side are fluidly separated via the seal member S2. And the coil spring 12 is arrange | positioned as an urging means which urges | biases piston 11 in the direction which shrinks fluid chamber CF. Therefore, a fluid having a predetermined pressure or higher that can resist the urging force of the coil spring 12 is accommodated in the fluid chamber CF. The plate 13 is a member that supports the coil spring 12, and is configured so that the coil spring 12 side in the cylinder 10a can communicate with the atmosphere through a hole 13a formed at the center thereof.
[0023]
Further, in the low pressure reservoir 10 of the present embodiment, a stepped recess made of recesses 11a and 11b is formed on the top surface of the piston 11 exposed to the fluid chamber CF so that the step 11b covers the recess 11b. A diaphragm member 14 is disposed and fixed by an annular member 15. A communication hole 11c is formed on the bottom surface of the recess 11b. Thereby, a space is formed between the diaphragm member 14 and the recess 11b, and the capacity space of the present invention is constituted by the enlarged space formed when the diaphragm member 14 is deformed inside the recess 11b. At this time, since the space between the diaphragm member 14 and the recess 11b is communicated with the atmosphere through the communication hole 11c, the fluid flowing into the fluid chamber CF is a minute pressure smaller than a predetermined pressure, and the diaphragm member 14 is recessed. Deforms to the inside of 11b. Thus, the fluid is accommodated in the enlarged space formed on the upper surface of the diaphragm member 14 under a minute pressure.
[0024]
Next, the operation of the pump device of the present embodiment having the above-described configuration will be described. When the drive cam 4 is driven to rotate about the shaft 3, the plunger 2 reciprocates in the hole 1a. Thus, when the plunger 2 moves to the right in FIG. 1, the compression chamber CP is expanded, the suction valve 7 is opened (the discharge valve 6 is in the closed position), and the fluid chamber CF of the low-pressure reservoir 10 is passed through the suction hole 7e. When the internal fluid (for example, brake fluid) is supplied, the fluid is introduced into the compression chamber CP through the suction valve 7 in the open position. When the plunger 2 moves to the left in FIG. 1, the compression chamber CP is reduced, the suction valve 7 is closed, the discharge valve 6 is opened, and the fluid in the compression chamber CP is discharged to the damper chamber DP. Is done.
[0025]
In the above operation, when the plunger 2 moves rightward from its top dead center (left end position), some fluid (brake fluid) is required until the spherical valve body 6b of the discharge valve 6 is seated on the seat member 6a. Is sucked into the compression chamber CP. Even if the suction valve 7 is in the closed position, the excess fluid flows out to the low pressure reservoir 10 side through the slit 7s of the suction valve 7. The fluid flowing out through the slit 7s in this way flows into the fluid chamber CF of the low-pressure reservoir 10, the diaphragm member 14 is deformed inside the recess 11b, and the fluid is accommodated in the enlarged space formed on the upper surface thereof. The Thus, the pressure in the compression chamber CP does not increase excessively as shown by the solid line in FIG. 31, and therefore noise generation via the plunger 2 can be suppressed.
[0026]
FIG. 2 shows another embodiment of the plunger-type pump device. Instead of the plunger 2 and the suction valve 7 of FIG. 1, a plunger 20 and a suction valve 70 are used, and these plunger 20 and the suction valve 70 are used. Thus, the low-pressure reservoir 10 is configured to communicate with the compression chamber CP. In this embodiment, the hole 1c which connects the compression chamber CP and the damper chamber DP is formed, and the discharge valve 60 is fitted in the hole 1c. A compression chamber CP is formed by a plug member 8 fixed to the housing 1, and a suction valve 70 is accommodated in the compression chamber CP.
[0027]
As shown in FIG. 2, the plunger 20 of the present embodiment is formed with an annular groove 21, an axial hole 22 that opens into the compression chamber CP, and a communication hole 23 that connects and connects these annular grooves. An annular seal member S3 is disposed on the compression chamber CP side around the center 21, and an annular seal member S4 is disposed on the drive cam 4 side. A fluid chamber CG formed by the annular groove 21 and the housing 1 is connected in communication with a fluid chamber CF (not shown in FIG. 2) of the low-pressure reservoir 10, as indicated by a one-dot chain line in FIG. The seal member S4 on the drive cam 4 side is a complete seal type made of rubber, but the seal member S3 on the compression chamber CP side is made of resin and is not a complete seal type, and allows a small amount of fluid to pass from the compression chamber CP. It is configured as follows. That is, the resin seal member S3 is fitted so as to have a slight gap with respect to the annular groove 24 of the plunger 20, as shown in an enlarged view in FIG. As shown in the lower part of FIG. 3, a flow path that allows passage of a small amount of fluid from the compression chamber CP is formed between the annular groove 24 and the seal member S3. Thus, in this embodiment, the outflow permitting means of the present invention is constituted by the seal member S3.
[0028]
In contrast to the configuration shown in FIGS. 1 and 2, the configuration of the low-pressure reservoir connected to the compression chamber CP through the suction valve 7 or through the suction valve 70 and the plunger 20 is the low-pressure reservoir shown in FIG. Not only the reservoir 10 but various low-pressure reservoirs described below can be used. 4 and 5 show a first embodiment of the low-pressure reservoir used in the present invention, which is the same as the low-pressure reservoir 10 shown in FIG. FIG. 4 shows a state before operating as the capacity means, and FIG. 5 shows a state where the capacity means operates. When the fluid flows into the fluid chamber CF, the diaphragm member 14 is deformed inside the recess 11b as shown in FIG. Thus, the fluid is accommodated in the enlarged space formed on the upper surface. The expanded space formed in this way constitutes the capacity space referred to in the present invention.
[0029]
Thus, the fluid in the enlarged space on the upper surface of the concave portion 11 b of the diaphragm member 14 is accommodated under a minute pressure due to the elastic deformation of the diaphragm member 14. That is, the stroke of the piston 11 with respect to the pressure in the fluid chamber CF of the low-pressure reservoir 10 has a relationship shown by a solid line in FIG. 26, and the stroke of the piston 11 does not exceed a predetermined pressure (Pb) as in the conventional low-pressure reservoir 10. I can't get it. However, in the present embodiment, as indicated by a broken line, the piston 11 has a minute pressure (Pa) smaller than a predetermined pressure (Pb) due to the action of the capacity means (diaphragm member 14 and recess 11b) on the pressure in the fluid chamber CF. The micro stroke (Da) is obtained, and a fluid having a micro pressure (Pa) is accommodated. If the pressure on the fluid chamber CF side decreases, the fluid corresponding to the enlarged space on the upper surface of the concave portion 11 b of the diaphragm member 14 is returned to the fluid chamber CF by the elastic force of the diaphragm member 14.
[0030]
6 and 7 show a second embodiment of the low-pressure reservoir used in the present invention. FIG. 6 shows a state before operating as a capacity means, and FIG. 7 shows a state where it operates as a capacity means. In the present embodiment, the diaphragm member 14 is formed integrally with the piston 11. For example, when the piston 11 is molded of resin, the diaphragm member 14 made of an elastic resin material is integrally molded. This eliminates the need for the annular member 15 in the embodiment of FIGS. 4 and 5, thereby reducing the number of components and the number of manufacturing steps. Since other configurations are substantially the same as those of the embodiment of FIGS. 4 and 5, the same reference numerals are assigned to substantially the same portions, and description thereof is omitted.
[0031]
FIGS. 8 and 9 show a third embodiment of the low-pressure reservoir used in the present invention. FIG. 8 shows a state before operating as a capacity means, and FIG. 9 shows a state where it operates as a capacity means. FIG. 10 is an enlarged view of a part of FIG. 9, and the hatching of the seal member S5 is omitted for easy explanation. In the present embodiment, the seal member S5 fitted into the annular groove 16 formed on the outer periphery of the piston 11 is formed in a shape different from the seal member S2 in the above-described embodiment, and the seal member S5 and the annular groove are formed. A predetermined space is formed between the two. That is, the seal member S5 constituting the annular elastic member of the present invention has a substantially X-shaped cross-sectional shape so that a predetermined space is formed when fitted into the annular groove 16 having a substantially rectangular cross section. Is set. Since other configurations are substantially the same as those of the embodiment of FIGS. 4 and 5, the same reference numerals are assigned to substantially the same portions, and description thereof is omitted.
[0032]
Thus, as shown in FIG. 9, when the fluid flows into the fluid chamber CF, the seal member S5 is pressed against one end side (the lower side in FIG. 9) of the annular groove 16 by the minute pressure, and the seal member S5. The portion in contact with the annular groove 16 is deformed so as to be in close contact with the inner surface of the annular groove 16, and an enlarged space CL is formed as shown in FIG. 10, thereby forming the capacity space referred to in the present invention. Therefore, the fluid flows into the space in the annular groove 16 including the enlarged space CL, but is stored under a minute pressure due to the elastic deformation of the seal member S5. That is, as shown by a broken line in FIG. 26, the piston 11 has a minute pressure (Pa) smaller than a predetermined pressure (Pb) by the action of the capacity means (the seal member S5 and the annular groove 16) on the pressure in the fluid chamber CF. A stroke (Da) is obtained and a fluid with a minute pressure (Pa) is accommodated. If the pressure on the fluid chamber CF side decreases, the fluid in the expanded space CL is returned to the fluid chamber CF by the elastic force of the seal member S5. In the present embodiment, the low-pressure reservoir has the same structure as the conventional one, and it is only necessary to accommodate the seal member S5, so that the manufacture is easy.
[0033]
11 and 12 show a fourth embodiment of the low-pressure reservoir used in the present invention. FIG. 11 shows a state before operating as a capacity means, and FIG. 12 shows a state where it operates as a capacity means. 13 is an enlarged view of a part of FIG. 12, and the hatching of the seal member S6 is omitted for easy explanation. Also in this embodiment, the capacity space referred to in the present invention is constituted by an enlarged space (indicated by CL in FIG. 13) formed between the seal member S6 and the annular groove 16 as in the embodiment of FIGS. However, it is formed in a shape different from the seal member S5 in the embodiment of FIGS. That is, the seal member S6 constituting the annular elastic member of the present invention has a substantially U-shaped cross-sectional shape so that a predetermined space is formed when fitted into the annular groove 16 having a substantially rectangular cross section. Is set.
[0034]
Thus, as shown in FIG. 12, when the fluid flows into the fluid chamber CF, the seal member S6 is pressed against one end side (the lower side in FIG. 12) of the annular groove 16 by the minute pressure, and the seal member S6. The portion in contact with the annular groove 16 is deformed so as to be in close contact with the inner surface of the annular groove 16, and the fluid in the annular groove 16 including the enlarged space CL formed thereby is minute pressure due to elastic deformation of the seal member S 6. Housed under. That is, as shown by a broken line in FIG. 26, a minute stroke (Da) of the piston 11 is obtained with a minute pressure (Pa), and a fluid with a minute pressure (Pa) is accommodated. Since other configurations are substantially the same as those of the embodiment of FIGS. 8 and 9, substantially the same parts are denoted by the same reference numerals as those of FIGS. 8 and 9 and description thereof is omitted. Also in this embodiment, the low-pressure reservoir has the same structure as the conventional one, and it is only necessary to accommodate the seal member S6, so that the manufacture is easy.
[0035]
14 and 15 show a fifth embodiment of the low-pressure reservoir used in the present invention. FIG. 14 shows a state before operating as a capacitive means, and FIG. 15 shows a state where the low-pressure reservoir is operated as a capacitive means. In the present embodiment, an elastic member interposed between the piston 11 and the cylinder 10a is used as reverse biasing means for biasing the piston 11 in the reverse direction with respect to the biasing direction of the coil spring 12. . In this embodiment, the disc spring 17 is used as the elastic member, the relative biasing force of the disc spring 17 with respect to the coil spring 12 is adjusted, and the capacity space of the present invention is expanded by the enlarged space when the fluid chamber CF is enlarged. Is going to be configured.
[0036]
Thus, at the time of non-operation shown in FIG. 14, the clearance between the piston 11 and the inner wall of the cylinder 10a is adjusted to be D1 by the biasing force of the disc spring 17 with respect to the biasing force of the coil spring 12. When the minute pressure of the fluid flowing into the fluid chamber CF is applied, the fluid chamber CF is expanded and the clearance becomes D2 as shown in FIG. 15, and the fluid is caused by the relative biasing force of the disc spring 17 with respect to the coil spring 12. It will be accommodated under minute pressure. That is, the stroke of the piston 11 with respect to the pressure in the fluid chamber CF of the low-pressure reservoir 10 in the present embodiment is as shown in FIG. 27, and the micro stroke (Db) of the piston 11 with a micro pressure (Pa) smaller than a predetermined pressure (Pb). And a fluid with a minute pressure (Pa) is accommodated. In the present embodiment, the piston 11 has the same structure as that of the prior art, and it is only necessary to secure a space for accommodating the disc spring 17, so that the manufacturing is easy. Since other configurations are substantially the same as those of the embodiment of FIGS. 4 and 5, the same reference numerals are assigned to substantially the same portions, and description thereof is omitted.
[0037]
FIGS. 16 and 17 show a sixth embodiment of the low-pressure reservoir used in the present invention. FIG. 16 shows a state before operating as a capacity means, and FIG. 17 shows a state operating as a capacity means. This embodiment also uses an elastic member interposed between the piston 11 and the cylinder 10a as reverse biasing means for biasing the piston 11 in the reverse direction with respect to the biasing direction of the coil spring 12. . In the present embodiment, the coil spring 18 is used as the elastic member, the relative urging force of the coil spring 18 with respect to the coil spring 12 is adjusted, and the capacity space of the present invention is expanded by expanding the fluid chamber CF. Is going to be configured.
[0038]
Thus, at the time of non-operation shown in FIG. 16, the clearance between the piston 11 and the inner wall of the cylinder 10a is adjusted to be D3 by the biasing force of the coil spring 18 with respect to the biasing force of the coil spring 12. When the minute pressure of the fluid flowing into the fluid chamber CF is applied, the fluid chamber CF is expanded and the clearance becomes D4 as shown in FIG. 17, and the fluid is caused by the relative biasing force of the coil spring 18 with respect to the coil spring 12. It will be accommodated under minute pressure. That is, also in this embodiment, the stroke of the piston 11 with respect to the pressure in the fluid chamber CF of the low-pressure reservoir 10 has the relationship shown in FIG. 27, and a fluid with a minute pressure (Pa) is accommodated. In the present embodiment, the piston 11 has the same structure as the conventional one, and a coil spring 18 that can easily adjust the biasing force can be used as the reverse biasing means. However, the piston 11 faces the piston 11 and communicates with the fluid chamber CF. It is necessary to form the enlarged diameter portion 1d for accommodating the coil spring 18 at the position. Since other configurations are substantially the same as those of the embodiment of FIGS. 4 and 5, the same reference numerals are assigned to substantially the same portions, and description thereof is omitted.
[0039]
18 and 19 show a seventh embodiment of the low-pressure reservoir used in the present invention. FIG. 18 shows a state before operating as a capacitive means, and FIG. 19 shows a state operating as a capacitive means. This embodiment also uses an elastic member interposed between the piston 11 and the cylinder 10a as reverse biasing means for biasing the piston 11 in the reverse direction with respect to the biasing direction of the coil spring 12. . In the present embodiment, an elastic resin ring 19 is used as the elastic member, the relative urging force of the elastic resin ring 19 with respect to the coil spring 12 is adjusted, and the expansion space when the fluid chamber CF is expanded is used as an expansion space. A capacity space is to be constructed.
[0040]
Thus, at the time of non-operation shown in FIG. 18, the clearance between the piston 11 and the inner wall of the cylinder 10a is adjusted to D5 by the biasing force of the elastic resin ring 19 against the biasing force of the coil spring 12. However, when a minute pressure of the fluid flowing into the fluid chamber CF is applied, the fluid chamber CF is expanded, the clearance becomes D6 as shown in FIG. 19, and the fluid is relatively attached to the coil spring 12 of the elastic resin ring 19. It is housed under a minute pressure due to power. That is, also in this embodiment, the stroke of the piston 11 with respect to the pressure in the fluid chamber CF of the low-pressure reservoir 10 has the relationship shown in FIG. 27, and a fluid with a minute pressure (Pa) is accommodated. Also in this embodiment, the piston 11 has the same structure as the conventional one, and it is only necessary to secure a space for accommodating the elastic resin ring 19, so that the manufacturing is easy. Since other configurations are substantially the same as those of the embodiment of FIGS. 4 and 5, the same reference numerals are assigned to substantially the same portions, and description thereof is omitted.
[0041]
20 and 21 show an eighth embodiment of a low-pressure reservoir used in the present invention. FIG. 20 shows a state before operating as a capacitive means, and FIG. 21 shows a state where it operates as a capacitive means. In the present embodiment, the piston 110 is formed with a sub cylinder 111 communicating with the fluid chamber CF, and the sub piston 112 is slidably accommodated in the sub cylinder 111. Accordingly, the sub-fluid chamber CS is formed in the sub-cylinder 111 to form the capacity space of the present invention and accommodate the fluid. As a sub urging means, a coil spring 113 is accommodated in the sub cylinder 111, and the sub piston 112 is urged by the coil spring 113 in the direction of reducing the sub fluid chamber CS.
[0042]
Thus, at the time of non-operation shown in FIG. 20, the sub piston 112 is held at the initial position of FIG. 20 by the biasing force of the coil spring 113, and the clearance between the sub piston 112 and the inner wall of the cylinder 10a becomes D7. However, when the fluid flows into the sub fluid chamber CS, the sub piston 112 is driven against the urging force of the coil spring 113, the sub fluid chamber CS is expanded, and the clearance becomes D8 as shown in FIG. The fluid is accommodated under a minute pressure by the urging force of the coil spring 113. That is, the stroke of the sub piston 112 with respect to the pressure in the fluid chamber CF of the low pressure reservoir 10 has a relationship shown by a solid line in FIG. 26, and the stroke of the piston 11 cannot be obtained until the pressure exceeds the predetermined pressure (Pb). As shown in the drawing, the minute stroke (Da) of the sub piston 112 is obtained with a minute pressure (Pa) smaller than a predetermined pressure (Pb), and the fluid with the minute pressure (Pa) is accommodated in the sub fluid chamber CS. When the pressure in the fluid chamber CF and thus the sub fluid chamber CS decreases, the sub piston 112 is returned toward the initial position by the biasing force of the coil spring 113, and the fluid in the sub fluid chamber CS is returned to the fluid chamber CF.
[0043]
In the present embodiment, the cylinder 10a and the like have the same structure as the conventional one, but the structure of the piston 110 of the present embodiment is different from the conventional piston structure. However, since the coil spring 113 that can easily adjust the urging force is used, the specification can be easily set. Since other configurations are substantially the same as those of the embodiment of FIGS. 4 and 5, the same reference numerals are assigned to substantially the same portions, and description thereof is omitted.
[0044]
22 and 23 show a ninth embodiment of the low-pressure reservoir used in the present invention. FIG. 22 shows a state before operating as a capacitive means, and FIG. In the present embodiment, a coil spring 114 for urging the piston 110 in a direction opposite to that of the coil spring 113 is provided with respect to the embodiment shown in FIGS. 20 and 21. It is possible to easily adjust the micro pressure of the fluid in the fluid chamber CS.
[0045]
Thus, in this embodiment, when the non-operation shown in FIG. 22 is performed, the sub piston 112 is held at the initial position, and the clearance between the sub piston 112 and the inner wall of the cylinder 10a is D9. Flows into the sub-fluid chamber CS, the sub-piston 112 is driven, the sub-fluid chamber CS is expanded, the clearance becomes D10 as shown in FIG. 23, and the fluid is subjected to a minute pressure due to the difference between the urging forces of the coil springs 113 and 114. Is housed in. That is, also in the present embodiment, as shown by a broken line in FIG. 26, a minute stroke (Da) of the sub piston 112 is obtained with a minute pressure (Pa) smaller than a predetermined pressure (Pb), and a minute amount is obtained in the sub fluid chamber CS. A fluid of pressure (Pa) is accommodated. Other configurations are substantially the same as those of the embodiment of FIGS. 20 and 21, and therefore, substantially the same parts are denoted by the same reference numerals as those of FIGS. 20 and 21 and description thereof is omitted. In the present embodiment, the urging force against the sub-piston 112 can be easily adjusted by the coil springs 113 and 114, so that the specification can be set more easily than in the embodiment of FIGS.
[0046]
24 and 25 show a tenth embodiment of a low-pressure reservoir used in the present invention. FIG. 24 shows a state before operating as a capacitive means, and FIG. 25 shows a state where it operates as a capacitive means. In the embodiment shown in FIGS. 20 and 21, the sub cylinder 111 and the like are accommodated in the piston 110, whereas in the present embodiment, they are accommodated in the housing 1. That is, in the embodiment shown in FIGS. 24 and 25, the housing 1 is formed with a sub cylinder 111 communicating with the fluid chamber CF, and the sub piston 112 is slidably accommodated in the sub cylinder 111. Accordingly, the sub-fluid chamber CS is formed in the sub-cylinder 111 to form the capacity space of the present invention and accommodate the fluid.
[0047]
As a sub urging means, a coil spring 113 is accommodated in the sub cylinder 111, and the sub piston 112 is urged by the coil spring 113 in the direction of reducing the sub fluid chamber CS. In addition, since the structure of piston 11 grade | etc., Is substantially the same as embodiment of FIG.4 and FIG.5, the code | symbol same as FIG.4 and FIG.5 is attached | subjected to substantially the same part, and description is abbreviate | omitted. Thus, also in the present embodiment, as shown by the broken line in FIG. 26, the minute stroke (Da) of the auxiliary piston 112 is obtained with the minute pressure (Pa) smaller than the predetermined pressure (Pb), and the inside of the auxiliary fluid chamber CS is obtained. A fluid having a minute pressure (Pa) is contained in the container. In this embodiment, the piston 11 has the same structure as the conventional one, and the capacity means of the present invention is separately formed in the housing 1, but the specification is easy to set.
[0048]
Thus, according to each of the above-described embodiments, the excess fluid in the compression chamber CP flows out to the low-pressure reservoir 10 side via each outflow permitting means even when the suction valve 7 is in the closed position. The capacity means is accommodated under a minute pressure. Therefore, the pressure in the compression chamber CP at the next top dead center does not increase excessively as shown by the solid line in FIG. The pressure rise in the compression chamber CP at this time increases as the amount of fluid ΔQ2 flowing out to the low-pressure reservoir 10 side becomes larger than the amount of fluid ΔQ1 flowing into the compression chamber CP via the discharge valve 6. Although the pressure in the compression chamber CP at the top dead center can be lowered, if ΔQ2 is too large, the pump efficiency is lowered. Therefore, it is desirable to set ΔQ1 and ΔQ2 to be substantially equal.
[0049]
The plunger pump device according to each of the above embodiments is suitable for a control device called an actuator for performing anti-skid control or the like in a vehicle hydraulic brake device, for example, but the present invention is not limited to this. Similarly, when applied to various fluid devices, noise during driving can be reduced.
[0050]
【The invention's effect】
Since this invention is comprised as mentioned above, there exist the following effects. That is, in the plunger type pump device of the present invention, as described in claim 1, there is provided an outflow permitting means for allowing a small amount of fluid to flow out from the compression chamber to the low pressure reservoir side even when the intake valve is in the closed position. A simple structure having a capacity space that can accommodate a minute amount of fluid that has flowed out of the outflow permission means, and that accommodates the fluid under a minute pressure that is smaller than a predetermined pressure, particularly for the operation of the discharge valve. The resulting noise of the pump device can be easily and reliably reduced.
[0051]
Further, in the apparatus according to claims 2 and 3, since the outflow permitting means can be configured with a slight modification to the existing apparatus, noise is reduced without causing an increase in the size of the apparatus. can do.
[0052]
Furthermore, in the apparatus according to claims 4 to 11, since the capacity means can be configured with a simple configuration, noise can be reduced without causing an increase in size of the apparatus.
[Brief description of the drawings]
FIG. 1 is a cross-sectional view showing a plunger-type pump device according to an embodiment of the present invention.
FIG. 2 is a cross-sectional view showing a pump device according to another embodiment of the present invention.
FIG. 3 is an enlarged cross-sectional view of a part of a pump device according to another embodiment of the present invention.
FIG. 4 is a cross-sectional view showing a first embodiment of a low-pressure reservoir used in the present invention.
FIG. 5 is a cross-sectional view showing a partially activated state of the low-pressure reservoir of the first embodiment.
FIG. 6 is a cross-sectional view showing a second embodiment of a low-pressure reservoir used in the present invention.
FIG. 7 is a cross-sectional view showing a partially activated state of the low-pressure reservoir of the second embodiment.
FIG. 8 is a cross-sectional view showing a third embodiment of a low-pressure reservoir used in the present invention.
FIG. 9 is a cross-sectional view showing a partially activated state of the low-pressure reservoir of the third embodiment.
10 is an enlarged cross-sectional view of a part of FIG.
FIG. 11 is a cross-sectional view showing a fourth embodiment of a low-pressure reservoir used in the present invention.
FIG. 12 is a cross-sectional view showing a partially activated state of the low-pressure reservoir of the fourth embodiment.
13 is an enlarged cross-sectional view of a part of FIG.
FIG. 14 is a cross-sectional view showing a fifth embodiment of a low-pressure reservoir used in the present invention.
FIG. 15 is a cross-sectional view showing a partially activated state of a low pressure reservoir according to a fifth embodiment.
FIG. 16 is a cross-sectional view showing a sixth embodiment of a low-pressure reservoir used in the present invention.
FIG. 17 is a cross-sectional view showing a partially activated state of the low-pressure reservoir of the sixth embodiment.
FIG. 18 is a cross-sectional view showing a seventh embodiment of a low-pressure reservoir used in the present invention.
FIG. 19 is a cross-sectional view showing a partially activated state of the low-pressure reservoir of the seventh embodiment.
FIG. 20 is a sectional view showing an eighth embodiment of a low pressure reservoir used in the present invention.
FIG. 21 is a cross-sectional view showing a partially activated state of the low-pressure reservoir of the eighth embodiment.
FIG. 22 is a sectional view showing a ninth embodiment of a low pressure reservoir used in the present invention.
FIG. 23 is a cross-sectional view showing a partially activated state of the low-pressure reservoir of the ninth embodiment.
FIG. 24 is a sectional view showing a tenth embodiment of a low pressure reservoir used in the present invention.
FIG. 25 is a cross-sectional view showing a partially activated state of the low-pressure reservoir of the tenth embodiment.
FIG. 26 is a graph showing the relationship of piston stroke to pressure in the fluid chamber of the low pressure reservoir in some embodiments of the invention.
FIG. 27 is a graph showing the relationship of piston stroke to pressure in the fluid chamber of the low pressure reservoir in the remaining embodiment of the invention.
FIG. 28 is an explanatory view showing an operating state of a general plunger type pump, and particularly showing a state where the plunger is at the top dead center.
FIG. 29 is an explanatory view showing an operating state of a general plunger-type pump, and particularly showing a state where the plunger moves from a top dead center to a bottom dead center.
FIG. 30 is an explanatory view showing an operating state of a general plunger type pump, and particularly showing a state where the plunger is directed to the next top dead center.
FIG. 31 is a graph showing a pressure state in a compression chamber corresponding to a position of a plunger in a general plunger type pump and the present invention.
[Explanation of symbols]
1 housing, 2,20 plunger, 3 shaft,
4 drive cam, 6,60 discharge valve, 7,70 intake valve,
10 low pressure reservoir, 11 piston, 14 diaphragm member,
S1 to S6 sealing member, CP compression chamber, CF fluid chamber,
CS secondary fluid chamber, CL expansion space, DP damper chamber

Claims (11)

  1. A housing that encloses the compression chamber; a plunger that is slidably accommodated in the housing and is disposed so that one end is exposed to the compression chamber; a driving means that reciprocates the plunger; and a communication connection to the compression chamber A plunger-type pump device comprising: a discharge valve that communicates with the compression chamber; and a low-pressure reservoir that contains fluid at a predetermined pressure or higher and communicates with the compression chamber via the suction valve. In the above, even when the suction valve is in the closed position, outflow permission means that allows a small amount of fluid to flow out from the compression chamber to the low pressure reservoir side, and a capacity that can accommodate the small amount of fluid that has flowed out of the outflow permission means A plunger-type pump device having a space and a capacity means for accommodating the fluid under a minute pressure smaller than the predetermined pressure.
  2. The suction valve has a valve seat and a valve body biased to be seated on the valve seat, and a slit is formed in at least one of the valve body and the valve seat. 2. The plunger type pump apparatus according to claim 1, wherein the permitting means is constituted.
  3. The plunger is slidably accommodated in the housing via a seal member that allows a small amount of fluid to pass from the compression chamber, and the outflow permission means is configured by the seal member. Item 2. A plunger-type pump device according to Item 1.
  4. A cylinder in which the low-pressure reservoir communicates with the compression chamber via at least the suction valve; a piston that slidably accommodates in the cylinder and forms a fluid chamber that accommodates fluid in the cylinder; 2. The plunger type pump device according to claim 1, further comprising an urging means for urging the piston in a direction of reducing the fluid chamber.
  5. A concave portion is formed on a surface of the piston exposed to the fluid chamber, the concave portion is covered with a diaphragm member, and an enlarged space formed in the fluid chamber when the diaphragm member is deformed inside the concave portion. 5. The plunger pump device according to claim 4, wherein a capacity space of the capacity means is formed.
  6. 6. The plunger type pump device according to claim 5, wherein the diaphragm member is formed integrally with the piston.
  7. An annular groove is formed on the outer periphery of the piston, and an annular elastic member is fitted to the annular groove so as to form a predetermined gap in the sliding direction of the piston. When the annular elastic member is deformed 5. The plunger type pump device according to claim 4, wherein a capacity space of the capacity means is constituted by an enlarged space formed between the annular elastic member and the annular groove.
  8. And a reverse urging means for urging the piston in a direction opposite to the urging direction of the urging means, and adjusting the relative urging force of the reverse urging means to the urging means to adjust the fluid chamber. The plunger-type pump device according to claim 4, wherein a capacity space of the capacity means is constituted by the expansion space.
  9. The plunger pump device according to claim 8, wherein the reverse biasing means is an elastic member interposed between the piston and the cylinder.
  10. The capacity means includes a sub-cylinder formed in the piston so as to communicate with the fluid chamber, and a sub-fluid chamber that slidably accommodates in the sub-cylinder and accommodates fluid in the sub-cylinder. 2. The plunger-type pump device according to claim 1, further comprising: a piston; and a sub urging unit that urges the sub piston in a direction in which the sub fluid chamber is contracted.
  11. The capacity means includes a sub-cylinder formed in the housing so as to communicate with the fluid chamber, and a sub-fluid chamber that slidably accommodates in the sub-cylinder and accommodates fluid in the sub-cylinder. 2. The plunger-type pump device according to claim 1, further comprising: a piston; and a sub urging unit that urges the sub piston in a direction in which the sub fluid chamber is contracted.
JP2001217536A 2001-07-18 2001-07-18 Plunger type pump device Expired - Fee Related JP4617617B2 (en)

Priority Applications (1)

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JP2001217536A JP4617617B2 (en) 2001-07-18 2001-07-18 Plunger type pump device
DE2002132384 DE10232384A1 (en) 2001-07-18 2002-07-17 Piston pump
US10/197,566 US20030021709A1 (en) 2001-07-18 2002-07-18 Plunger pump device

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WO2010046953A1 (en) * 2008-10-24 2010-04-29 パスカルエンジニアリング株式会社 Hydraulic pressure generation device
JP5513066B2 (en) * 2009-10-16 2014-06-04 株式会社イワキ Reciprocating pump and check valve
DE102009055228A1 (en) * 2009-12-23 2011-06-30 Robert Bosch GmbH, 70469 Piston pump for a hydraulic vehicle brake system
CN107237727A (en) * 2017-06-22 2017-10-10 武汉元丰汽车电控系统有限公司 A kind of oil return pump installation

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US20030021709A1 (en) 2003-01-30
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