JPS5835282A - Hydraulic pump - Google Patents

Abstract

PURPOSE:To facilitate the inspection and replacement of an oil filter by arranging the oil filter in a filter chamber in a pump main body so that the oil filter is held by a removable cap closing the aperture of the filter chamber. CONSTITUTION:A filter chamber 89 opening outward is formed near the bulkhead 73 of a pump main body 70, and the first through the third oil paths 83-85 are combined together in the filter chamber 89. An oil filter 90 is arranged in the filter chamber 89 so as to partition between the second oil path 84 provided with a suction valve 86 and the other first and third oil paths 83, 15, and the oil filter 90 is held by a removable cap 91 closing the aperture of the filter chamber 89. Therefore, the oil filter 90 can be easily inspected and replaced by removing the cap 91.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a hydraulic pump used in a braking device of a motorcycle, etc., and allows easy inspection and replacement of an oil filter disposed in a filter chamber within the pump body. It is an object of the present invention to provide the above-mentioned hydraulic pump, in which air can be easily vented from the pump chamber formed within the pump body.

As a means for achieving the first object, the present invention provides a pump body which is divided into an oil reservoir chamber and a pump chamber by a partition wall, and a fin that opens outward near the partition wall of the pump body.

A first oil passage and a second oil passage are provided in the partition wall to form a filter chamber, and communicate between the filter chamber and the oil reservoir chamber, and between the filter chamber and the pump chamber, respectively. An oil filter is arranged to partition the two oil passages, and the oil filter is held by a removable cap that closes the opening of the filter chamber, and the second oil passage operates only in one direction from the filter chamber to the pump. It is characterized by being equipped with a suction valve that allows oil to flow.

Hereinafter, an embodiment of the present invention will be described with reference to the drawings. In FIGS. 1 and 2, a motorcycle is equipped with a brake lever 1 on a steering handle H and a front manuta cylinder Af f operated by the brake lever 1. Further, the lower part of the vehicle body F is provided with a brake pedal 2 and a rear mask cylinder Mγ which can be operated by a braking input from either the brake pedal 2 or the brake lever 1. The input to the rear manuta cylinder Mr of the brake lever 1 is given as the output hydraulic pressure of the front mask cylinder Mf, and the input from the brake pedal 2 to the rear manuta cylinder Mr is mechanically transmitted, the details of which will be described later. do.

The rear mask cylinder Mr is connected via an oil passage 4 to two pairs of left and right hydraulic front wheel brakes Bf for braking the front wheels Ff, and a single hydraulic rear brake for braking the rear wheels Wr. The oil passage 5 is connected to Br by valve, and the oil passage 5
A known proportional pressure reducing valve V is interposed therein.

A horizontally opposed engine E is mounted on the vehicle body F in the middle of the front and rear wheels Wf and Wγ of the motorcycle, and at the rear of this engine E, during braking, the front wheel An anti-lock device At that automatically performs relaxation and recovery of the braking force of only the brake Bf is provided. Control No. 9 to this anti-lock device At is generated by a speed sensor S provided on the front wheel IP'f, and is generated by a signal processing device C.
The signal is then sent to the anti-lock device AL.

The structure of the valley portion will be further explained with reference to FIGS. 3 and 4.

The front manuta cylinder Mf is configured in a known single type. That is, one piston 8 operated by the brake lever 1 is slid into the cylinder hole 7 of the cylinder body 6, and the piston 8 connects the output port 10 of the hydraulic chamber 9 defined at the front part of the cylinder hole 7 with the rear part. An oil passage 11 that continues to the master cylinder Mγ is connected. Therefore, when the brake lever 1 is actuated to move the piston 8 forward, hydraulic pressure is generated in the hydraulic chamber 9, and the hydraulic pressure is output from the output port 10.
It is input to the rear mask cylinder Mr. Cylinder body 6
is integrally equipped with a reservoir 12 that can supply hydraulic oil to the hydraulic chamber 9.

The rear mask cylinder Mr is constructed in a tandem type, particularly as clearly shown in FIG. That is, a first cylinder hole 14 at the rear and a 27th ring hole 39 at the front are formed in the cylinder body 13 and are arranged coaxially with a fixed partition wall 16 in between. and second braking binuton15. .

15□ are slid together in front and rear series (in the figure, vertically in series), and in the first cylinder hole 14, the first brake piston 151 and the fixed partition wall 16 have a first brake hydraulic chamber 17. and both pistons 151.

15□ define a $2 brake hydraulic chamber 172 between them. First brake hydraulic chamber 17. The first output port 181 is opened in the side wall, and the second output port 182 is opened in the second brake hydraulic chamber 17□, and the first output port 181 is opened in the side wall.
An oil passage 4 connected to the front wheel brake Bf is connected to the second output boat 182, and an oil passage 5 connected to the rear wheel brake Br is connected to the second output boat 182.

The second brake piston 15 □ integrally includes a piston rod 15 □ a that slidably penetrates a sleeve 19 that is fitted and fixed to the lower end opening of the first cylinder hole 14 and projects to the outside. , this piston rod 15□ (z is connected to the brake pedal 2 via the push rod 2o,
When the brake pedal 2 is depressed, the second brake piston 15□ can be pushed forward (upward in the figure) via the push rod 20. 21 is a return spring for the brake pedal 2, and 22 is a stopper bolt for regulating the backward limit of the pedal 2, so that the backward limit of the pedal 2 can be adjusted.
It is screwed onto a bracket 23 extending from the vehicle body F.

Further, in the first cylinder hole 14, the second brake piston 15□ and the sleeve 19 have a hydraulic chamber 24 between them.
The oil passage 11 connected to the front mask cylinder Mf is connected to an input port 25 which has a diameter of Φi and opens on one side of the chamber 24, and when hydraulic pressure is applied to the hydraulic chamber 24 from the input port 25, the hydraulic pressure The second brake piston 152 can also be pushed forward.

The first and second brake hydraulic chambers 178, 17□ are provided with first and second brake pistons 151.15. The first and second springs 26. ．． 2
'6□ are accommodated respectively.1. Except for that, the second return spring 2
The set load of 62 is the first return spring 26. is set smaller than that of . First brake piston 15. A piston rod 151a protrudes from the front surface of the piston 151 and slidably passes through the partition wall 16 in order to restrict the retraction limit of the piston 151a.
A circlip-shaped stopper 27 that comes into contact with the upper surface of the partition wall 16 is locked at the tip of the partition wall 16 . Also, the second brake piston 1
In order to restrict the retraction limit of 5□, a circlip-shaped stopper 28 that comes into contact with the upper end surface of the sleeve 19 is engaged with the piston rod 15□α of the piston 15□.

The second return spring 262 is connected to a fixed seat plate 30 fixed to the second brake piston 152 by a bolt 29, and a movable seat that can slide on the bolt 29 with a limited stroke rotation. The movable seat plate 31 is compressed between the fixed seat plate 30 and the fixed seat plate 30, so that both brake pistons 1
5. , 152 are at the retraction limit, they substantially abut against the lower end of the first brake piston 151.

First and second brake pistons 15. ．． 152 is a piston cup 32 on each front surface. ．． 32□ are attached to each, and the middle part is made small diameter and the replenishment oil chamber 33. ．． 332
These oil chambers 331 and 332 are respectively formed in the piston cup 32.

Oil supply holes 341 and 34□, which communicate with the 32□ valley back ribs, are bored in the valley braking pistons 151 and 152, respectively.

The cylinder body 13 has a first oil passage 36 communicating with an oil passage 35 connected to the reservoir R. The second cylinder hole 14.39 is bored parallel to both brake pistons 15.39. ,152
When the piston cups 32 are located at the retraction limit,
．． ．． Immediately before 322, the first and second brake hydraulic chambers 17. , t72
Relief ports 37I and 372 open respectively in
A supply boat 38t = 382, which is always open to the replenishment oil chambers 33□ and 332, communicates with the oil passage 36.

The second cylinder hole 39 is formed in the cylinder cap 13α constituting the front end of the cylinder body 13, and a control piston 40fJ' having a piston cup 41 on the front side is slid into this cylinder hole 39, and the piston 4o
is opposed to the tip of the piston rod 15, α, of the first brake piston 15°.

The control piston 40 is inserted into the second cylinder hole 39 at the front side.
The partition wall 1 is divided into a control oil pressure chamber 42 and a rear replenishment oil chamber 43, and a return spring 44 contracted in the control oil pressure chamber 42
6 is normally held at the retraction limit. Supply oil room 43
communicates with the reservoir R via the oil passage 35 similarly to the replenishment oil chambers 331, 332, and connects the chamber 43 with the piston cup 41.
The control piston 40 is provided with an oil supply hole 45 that communicates with the back surface of the control piston 40 . In addition, 46 and 47 in FIG. 4 are air bleeders.

The anti-lock device At includes the control piston 40, a pair of normally-closed electromagnetic control valves 48 and 49 that control the operation of the control piston 40, and the control piston 4.
It is composed of a pressure accumulator ΔC that stores 0 working oil pressure and a hydraulic pump P that supplies pressure oil to this pressure accumulator Ac. The normally-closed control valve 48 is connected to an oil passage 50 connecting the hydraulic pump P and the pressure accumulator Ac to the control hydraulic chamber 42, and also connected to the normally-opened control valve 4.
9 is an oil passage connecting the reservoir R and the control oil production room 42;
1 respectively. In addition, 52°53.5 in Figure 3
4 is an oil filter provided before and after the control valves 48 and 49;
55 is an oil filter provided immediately after the hydraulic pump P.

Next, the hydraulic pump P will be explained.

The hydraulic pump P is mounted on the outer surface of the engine E, and its mounting position is between a pair of engine blocks Ea and 'Eb that protrude to the left and right of the horizontally opposed engine E, as shown in Fig. 2. , which is located toward the front of the vehicle, is behind the right engine block Eb in the illustrated example, so that the dead space Ds behind the right engine block Eb based on the displacement ε of both engine blocks Eα and Eh in the vehicle longitudinal direction is closed to the hydraulic pump P. It is effectively used for the installation of

In addition, the hydraulic pump P, as shown in FIGS. 5 and 6,
It is attached to the engine body 61 so as to be driven by the valve drive camshaft 60 of the engine block Eb.

The inside of the pump body 70 of this hydraulic pump P is accessed from above by a pair of upper and lower partition walls 73 and 74, which serve as an oil reservoir and spring chamber 75.
The oscilloscope is divided into a pump chamber 76 and an operating chamber 77. The working chamber 77 is provided with a distal end portion of a pump drive shaft 71 having a relatively small diameter and fixed to the outer end of the valve drive camshaft 60 . The distal end thereof is formed into an eccentric pin 71α, into which a ball bearing serving as an eccentric cam 72 is fitted, and the lower end of the tappet 78 engages with the outer peripheral surface of the cam. Tappet 78
The plunger 7 slidably penetrates the partition wall 74 and enters the pump chamber 76, and slideably penetrates the partition wall 73.
It touches the lower end of 9. The shaft diameter of the tappet 78 is formed to be sufficiently small compared to the diameter of the plunger 79. The upper end of the plunger 79 that has entered the spring chamber 75 and the spring chamber 75
A movable seat plate 80 and a fixed seat plate 81 are attached to the ceiling wall, respectively, and a spring 82 is installed between these two seat plates 80 and 81 to apply a constant set load.

The spring chamber 75 communicates with the reservoir R via the oil passage 56, and the pump chamber 76 communicates with the pressure accumulator Ac via the oil passage 50.

The partition wall 73 is provided with first and second oil passages 83 and 84 that communicate between the spring chamber 75 and the pump chamber 76, and the second oil passage 84 allows fluid to flow in only one direction from the spring chamber 75 to the pump chamber 76. A one-way valve, that is, a suction valve 86, is provided to allow fluid to flow in only one direction from the pump chamber 76 to the pressure accumulator AC in the flow path in the joint 87 that connects the pump chamber 76 and the oil path 50. A one-way valve, ie, a discharge valve 88, is provided to allow for.

Further, the partition wall 73 is provided with a third oil passage 85 for communicating between the spring chamber 75 and the working chamber 77, so that the working oil flowing into the spring chamber 75 is introduced into the working chamber 77 as lubricating oil. It has become.

Furthermore, a filter chamber 89 that opens outward is formed near the partition wall 73 of the pump body 70.
9, the first to third oil passages 83 to 85 merge. This filter chamber 89 includes a second oil passage 84 provided with a suction valve 86 and a first oil passage 84 provided with a suction valve 86 . An oil filter 90 is arranged to partition the third oil passages 83 and 85, and is held by a removable cap 91 that closes the opening of the filter chamber 89. Therefore, the suction valve 86 can always send the hydraulic oil filtered by the oil filter 90 to the pump chamber 76. Furthermore, by removing the cap 91, the oil filter 90 can be easily inspected and replaced, and the air in the pump chamber 76 can also be easily vented by manually opening the suction valve 86. Note that 92 in FIG. 6 is a drain bolt for the working chamber 77.

The pump body 7θ has an annular positioning protrusion 70α integrally formed on one side that concentrically surrounds the pump drive shaft 71, and this protrusion 70α accommodates the oil seal 62 at the outer end of the valve drive camshaft 60. It is fitted into a seal housing 63 formed on the engine main body 61 for this purpose. This convex portion 70α also serves to transmit and support the operational reaction force of the eccentric cam 72 applied to the pump body 70 to the engine body 61. After the positioning protrusion 70a is fitted, the pump body IO is fixed to the engine body 61 with bolts 93 with its upper end, that is, the spring chamber 76 side, moved toward the center of the engine E, as shown in FIG. Ru. As a result, the hydraulic pump P is moved to the engine block E.
b, so that it does not become a useless protrusion to the side of the vehicle, and the oil passage connected to the hydraulic pump P can be shortened.

An annular seal retainer 95 is fitted to the inner peripheral surface of the positioning convex portion 70a via a seal ring 94, and an oil seal 96 of the pump drive shaft 71 is fitted to the inner peripheral surface of this seal retainer 95. The seal retainer 95 has an outward flange 95α at the inner end.

An inward flange 91 is integrally provided at the outer end, and the outward flange 95a connects the seal retainer 95 to the pump drive shaft 7.
1 and is fitted into the C seal housing 63 and held between the positioning convex portion 71E and the oil seal 62. The inward flange 95h is disposed between the eccentric cam 72 and the oil seal 96 as a retaining member for leaving the seal retainer 95 on the pump drive shaft 71 side when the pump main body 70f) is removed.

Therefore, since the oil seals 62 and 96 are always held on the valve drive camshaft 6D and the pump drive shaft 71 by the seal retainer 95, there is no possibility that they may come off and be damaged when the pump body 70 is attached or detached. No oil leakage outside. In addition, the pump drive shaft 71 is formed to have a smaller diameter than the valve drive camshaft 60, and the sliding speed with respect to the oil seal 96 during rotation is kept low, so the oil seal 96 has good durability and a long life. Leakage of the hydraulic oil in the working chamber 77 can be prevented over a period of time.

Also, when installing the hydraulic pump P, as shown in Figure 5,
The engagement position between the eccentric cam 12 and the tappet 18 of the hydraulic pump P is between the valve drive camshaft 60 of the engine E and the intake rocker blade.
The exhaust rocker arm 64 and the exhaust rocker arm 65 are arranged so that the phase on the circumference is slightly shifted with respect to each engagement position. If you do this, the valve train cam II! The load applied to the 1jI 60 and the bearing 66 supporting it is dispersed, which is advantageous in terms of durability. In the figure, reference numerals 67 and 68 indicate intake and exhaust valves that are opened from the valve drive camshaft 60 via rocker arms 64 and 65.

Next, the operation of this embodiment will be explained.

First, in FIGS. 3 and 4, when the front mask cylinder Mf is actuated by the brake lever 1, its hydraulic chamber 9
The extraction pressure generated in 19 and is not transmitted to the bushing rod 20.

Further, when the brake pedal 2 is depressed, the pedal force is mechanically inputted to the second brake piston 15□ via the bushing rod 20, and thereby the second brake piston 15□
is pushed in the forward direction.

Along with this, the hydraulic oil in the reservoir 12 of the front mask cylinder Mf is only sucked into the hydraulic chamber 24 whose volume increases through the hydraulic chamber 9 and the oil passage 11, and no reaction force acts on the brake lever 1. do not.

Therefore, brake leno (-1 and brake pedal 2
As soon as 1 front mask cylinder M is operated at the same time,
The sum of the pressing force by the output oil pressure of f and the pressing force by the push rod 20 is applied to the second brake piston 15□ as a braking input.

Then, when the second brake piston 152 receives the brake input as described above, the first and second brake pistons 15□, 1
52 are first and second return springs 261;

262, moving forward while compressing the piston cups 32. ．． 322 is the relief port 37. '.

312 and then each brake piston 15I.

152, the first and second brake hydraulic chambers 17,
．． 172, the hydraulic pressure generated in the first brake hydraulic chamber 1F+ is transmitted from the first output port 18I to the front wheel brake Bf through the oil passage 4 to operate it, and is transferred to the second brake hydraulic chamber 112. The generated hydraulic pressure is transmitted from the second output port 18□ to the rear wheel brake By through the oil path 5 to operate it, and braking force is applied to the front and rear wheels Ff't/J'r, respectively.

and 9, as mentioned above, the 0 set load of the second return spring 26□ is set smaller than that of the first return spring 26□, so when the second brake piston 152 is initially moved, the first brake piston 151 is Prior to forward movement, the second return spring 26□ is compressed, and hydraulic pressure is first generated in the second brake hydraulic chamber 11□. Then, after the oil pressure reaches a certain value Pl, the first return spring 26 is compressed, the first brake piston 151 starts moving forward, and oil pressure is generated in the first brake oil pressure chamber 171.

In addition, since a known proportional pressure reducing valve V is provided in the oil passage 5 between the output port 1B□ of the second brake hydraulic pressure chamber 112 and the rear wheel brake Br, the output oil pressure of the second output port 18□ is set to a predetermined value. When the pressure rises to 13 or more, the output oil pressure is reduced at a fixed ratio by the action of the proportional pressure reducing valve V, and the rear wheel brake B is
transmitted to T. On the other hand, the first brake hydraulic chamber 17. The output port 18I and the oil passage 4 of the front wheel brake pedal are always in a conductive state, and the output hydraulic pressure of the first output boat 181 is directly transmitted to the front wheel brake Bf.

As a result, the braking pressures of the rear wheel brakes Bf and BT increase along the braking hydraulic pressure distribution line AKG shown in FIG. 7. This characteristic approximates the ideal braking oil pressure distribution curve B of a motorcycle, and allows the rider to easily perform efficient braking.

During braking, as the first brake piston 151 moves forward, its piston rod 15. Although the control m1 piston 40 is also advanced through α, normally the control hydraulic chamber 42 is operated by the normally open control valve 49.
Since the hydraulic fluid in the control hydraulic chamber 42 is discharged to the reservoir R side as the control piston 40 moves forward, it hardly acts as a resistance to braking input.

If the front wheel Wf attempts to lock due to braking, the signal processing device C shown in FIG.
A valve close signal is sent to the normally open control valve 49 in the figure, and a valve open signal is sent to the normally closed control valve 48.

When these control valves 48 and 49 operate according to the above-mentioned signals, the oil passage 51 is shut off and the oil passage 5o is made conductive, so that pressure oil flows from the pressure accumulator A'c to the control hydraulic chamber 42 through the oil passage 50. The control piston 40 moves the first brake piston 151 slightly backward against the braking input, thereby reducing the pressure inside the first brake hydraulic chamber 11. As a result, the braking force of the front wheel brake Bf is reduced, and the locking phenomenon of the front wheel If is avoided.

Then, the signal processing device C detects this situation and returns both control valves 48 and 49 to their normal positions, thereby reducing the pressure in the control hydraulic chamber 42. As a result, the braking force of the front wheel brake Bf increases again, and by repeating the above operations at high speed, the front wheel 11'f is efficiently braked without locking.

The first brake piston 15□ by actuation of the control piston 40
Conversely, the rear wheel brake B increases the pressure in the second brake hydraulic chamber 11□, but this increase in pressure is instantaneous.
The force is absorbed by the elastic deformation of each part of the T's hydraulic system, and the resulting force does not impair the operating sensation of the brake lever 1 and brake pedal 2.

In this way, even while the anti-lock device At is controlling the braking force of the front wheel brake Bf, the braking force of the rear wheel brake Br can be freely adjusted by adjusting the braking input to the second brake piston 152. I can do it.

When the brake lever 1 and brake pedal 2 are released to release the braking of the front wheel tl'f and the rear wheel Wr, the first.
Due to the elastic force of the second return springs 26□ and 262, the first return spring. The second brake piston 151,152 retreats, and the first brake piston 151,152 moves back. Second brake hydraulic chamber 11□.

1. When the pressure inside 331.12 is reduced to below atmospheric pressure, the replenishment oil chamber 331. Due to the pressure difference inside the piston cup 332, the outer periphery of the piston cup 321.322
2 to provide a gap between the inner wall of the first cylinder hole 14 and the replenishment oil chamber 33.

332 to oil supply hole 34. ．． 34□ to each brake-hydraulic chamber 171, 172, and the excess oil is returned to the oil path 35 from each relief port 371, 372, and thus to the reservoir R. During this time, each replenishment oil chamber 33. ，
332 is connected to a supply port 38 by an oil passage 36. ．． 38
It is refueled through 2.

On the other hand, when the control piston 40 is retracted, oil is supplied to the control hydraulic chamber 42 through the oil supply hole 45 from the replenishment oil chamber 43 by the same action as described above. Therefore, especially as the control piston 40 reciprocates, oil circulation occurs in the path of the control hydraulic chamber 42, oil passage 51, reservoir R1 oil passage 35, replenishment oil chamber 43, oil supply hole 45, and control hydraulic chamber 42. ,
It is possible to prevent air bubbles from remaining in the control hydraulic system including the control hydraulic chamber 42.

Next is the action of the hydraulic pump P. In FIGS. 5 and 6, when the valve drive camshaft 60, and therefore the pump drive shaft 11, rotates due to the operation of the engine E, the eccentric cam 12, which moves eccentrically at the same time, is moved by the spring 82. Tappet 18 in collaboration with
and gives vertical reciprocating motion to the plunger 79. Due to these reciprocating movements, the volume of the pump chamber 76 repeatedly expands and contracts, and at the time of expansion, the suction valve 86 opens due to the reduced pressure in the pump chamber 76, so that the oil supplied from the reservoir R to the spring chamber 75 is The pressure oil is sucked into the pump chamber 76, and when the pump chamber 76 contracts, the pressure in the pump chamber 76 is increased to open the discharge valve 88, and the pressure oil is supplied from the pump chamber 16 to the pressure accumulator 4c. When the hydraulic pressure in the pressure accumulator Ac increases and reaches a certain value, the hydraulic pressure in the pump chamber 76 also shows a similar value, and the upward force of this hydraulic pressure on the plunger 79 is the downward force of the spring 82, that is, the cent load. In balance, the plunger T9 is held near the upper limit of the rise by the tappet 78, and only the tappet 7B follows the movement of the eccentric cam 72 and repeats the vertical movement.

In this case, since the force for pressing down the tappet 78 is applied from the hydraulic pressure in the pump chamber 76, the suction valve 86 is kept closed by the hydraulic pressure in the pump chamber 76 even when the tappet 78 is lowered. In this way, the hydraulic pump P stops its pumping action and does not apply unnecessary load to the engine E (. Note that the pressing force due to the hydraulic pressure in the pump chamber 76 acts on the engagement surface between the tappet 78 and the eccentric cam 72. However, since the shaft diameter of the tappet 78 is sufficiently small, the pressing force is slight and can be ignored as a load on the engine E.

As described above, according to the present invention, the inside of the pump main body is divided into an oil reservoir chamber and a pump chamber by a partition wall.

A filter chamber that opens outward is formed near the partition wall of the main body,
First and second oil passages communicating between the filter chamber and the oil reservoir chamber, and between the filter chamber and the pump chamber, respectively, are provided in the partition wall, and the first oil passage and the second oil passage are partitioned into the filter chamber. An oil filter is arranged, the oil filter is held by a removable cap that closes the opening of the filter chamber, and a suction valve is provided in the second oil passage that allows hydraulic oil to flow in only one direction from the filter chamber to the pump chamber. Since this is provided, the oil filter can be easily inspected and replaced by removing the camp, and the air in the pump chamber can be easily vented by manually opening the suction valve.

[Brief explanation of the drawing]

The drawings show an embodiment of a braking device equipped with a hydraulic pump of the present invention, in which FIG. 1 is a transparent side view of a motorcycle equipped with the braking device, FIG. 2 is a plan view of the same, and FIG. 3 is a diagram showing a brake system. The hydraulic circuit diagram of the device, Fig. 4 is an enlarged longitudinal sectional side view of the rear mask cylinder in the braking device, and Fig. 5 is an enlarged longitudinal sectional rear view of the hydraulic pump in the braking device in a state where it is attached to the engine.
Fig. 6 is a sectional view taken along the VI-Vl line in Fig. 5, and Fig. 7 is a characteristic diagram of the braking oil pressure distribution ratio of the rear wheel brake, where line A indicates the characteristic due to the braking device and dB indicates the ideal characteristic. It is something. P... Hydraulic pump, 70... Pump body, 73... Bulkhead, 7,5...
Oil reservoir and spring chamber, 76...Pump room, 83.84...
・1st ° 2nd oil passage, 86... Suction valve, 89... Filter chamber, 90... Oil filter, 91... Cap Patent applicant Honda Motor Co., Ltd.

Claims (1)

[Claims] The inside of the pump body is divided into an oil reservoir chamber and a pump chamber by a partition wall, and a filter chamber that opens outward is formed in the vicinity of the partition wall of the bong body. first and second oil passages communicating between the filter chamber and the pump chamber, respectively, are provided in the partition wall, and an oil filter is arranged in the filter chamber so as to partition between the first oil passage and the second oil passage, The oil filter is protected by a taxable camp that closes the opening of the filter chamber, and the second oil passage has a suction that allows cooling of the hydraulic oil only in one direction from the filter chamber to the pump chamber. A hydraulic pump equipped with a valve.