JPS5835281A - Hydraulic pump - Google Patents

Abstract

PURPOSE:To utilize an existing rolling bearing as an eccentric cam by constituting the eccentric cam provided on a pump drive shaft with the rolling bearing fitted to an eccentric pin protruding from the end face of the pump drive shaft. CONSTITUTION:The tip of a pump drive shaft 71 is formed into an eccentric pin 71a, to which is fitted a rolling bearing that constitutes an eccentric cam 72. According to this constitution, during the eccentric movement of the eccentric cam 72 which moves a plunger 79 reciprocally, the outside lace 72a of the eccentric cam 72 is applied a spring force of a spring 82 through the plunger 79 and is scarcely rotated, thereby the sliding between the extra small shaft section 78b of the plunger 79 and the outside lace 72a is suppressed to the utmost and the wear of the coupling section of them can be prevented.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a plunger-type hydraulic pump used in a braking device of a motorcycle, etc., and it simplifies the configuration of an eccentric cam that reciprocates the plunger, and also improves the alignment of both images of the plunger and the eccentric cam. It is an object of the present invention to provide a hydraulic pump as described above, which can prevent wear of the parts and improve the durability of both parts.

As a means for achieving the above object, the present invention provides a plunger slidably within the pump body, one end of the plunger is engaged with the outer peripheral surface of an eccentric cam provided on the pump drive shaft, and the plunger is disposed within the pump body. The present invention is characterized in that a spring is disposed to bias the eccentric cam toward the outer peripheral surface thereof, and the eccentric cam is constituted by a rolling bearing fitted to an eccentric pin protruding from the end surface of the pump drive shaft.

Hereinafter, an embodiment of the present invention will be described with reference to the drawings. In FIG. The lower part of the vehicle body F is equipped with a brake pedal 2 and a rear mask cylinder Mγ that can be actuated by a braking input from either the brake pedal 2 or the brake reno (-1). The input from the brake pedal 2 to the rear mask cylinder Mr (is given as the output hydraulic pressure of the front mask cylinder Mf), and the input from the brake pedal 2 to the rear mask cylinder Mr is mechanically transmitted, the details of which will be described later. do.

The rear mask cylinder M r is connected via an oil passage 4 to a pair of left and right hydraulic front wheel brakes Bf for braking the front wheels Wf, and a single hydraulic rear wheel brake Bγ for braking the rear wheels Wr. The oil passage 5 is connected to the oil passage 5 through an oil passage 5, and a known proportional pressure reducing valve V is interposed in the oil passage 5.

A horizontally opposed engine E is mounted on the vehicle body F in the middle of the front and rear wheels Wf and Fγ of the motorcycle, and an engine E is installed at the rear of the engine E to control the operation of the rear mask cylinder Afr during braking. Relaxation of braking force of front wheel brake Bf only,
An anti-lock device At is provided which automatically performs the recovery. The control signal to this anti-lock device At is transmitted to the front wheel If
The signal is generated by a speed sensor 5 installed at the front end of the vehicle, and is sent to the anti-lock device At via a signal processing device C.

The configuration of each of the above parts will be further explained with reference to FIGS. 3 and 4.

The front mask cylinder Aff is configured in a known cinder type. That is, one piston 8 operated by the brake lever 1 is slidably connected to the cylinder cylinder L7 of the cylinder body 6, and the output port 10 of the hydraulic chamber 9 defined in the front part of the cylinder hole I is connected by this piston 8. to the rear mask cylinder K
11 oil lines connected to l r are 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 transferred to the output port 10.
It is output from the rear mask cylinder Mγ and input to the rear mask cylinder Mγ.

The 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, as shown in particular in FIG. That is, a first cylinder hole 14 at the rear and a second cylinder 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 a second brake piston 151.

152 are slid together in front and back series (in the figure, vertically in series), and in the first cylinder hole 14, the first brake piston 15□ and the fixed partition wall 16 define a first brake hydraulic chamber 17□ therebetween, Both pistons 151 and 152 also define a second brake hydraulic chamber 172 between them. First brake hydraulic chamber 17
1 is the first output port 18, and the second brake hydraulic chamber 17
2 has a second output port 182 opened in the first wall of each side, and a front wheel brake Bf is connected to the first output port 18□.
An oil passage 4 connected to the rear wheel brake Br is connected to the second output port 182, and an oil passage 5 connected to the rear wheel brake Br is connected to the second output port 182.

The second brake piston 152 is integrally formed with a piston rod 152a that slidably passes through the sleeve 19 and is fitted into and fixed to the lower end opening of the first cylinder hole 14 and protrudes to the outside. 152a is connected to the brake pedal 2 via the bushing rod 20, and when the brake pedal 2 is depressed, the second brake piston 152 can be pushed forward (upward in the figure) via the bushing rod 20. There is. 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, which is screwed onto a bracket 23 extending from the vehicle body F so that the backward limit of the pedal 2 can be adjusted. I'm 1 year old.

Further, in the first cylinder hole 14, the second brake piston 152 and the sleeve 19 define a hydraulic chamber 24 therebetween, and an input port 25 opening on one side of the chamber 24 is connected to the front mask cylinder Mf. When the oil passage 11 connected to the input boat 25 is connected and hydraulic pressure is applied to the hydraulic chamber 24 from the input boat 25, the second brake piston 152 can also be pushed forward by the hydraulic pressure.

First and second return springs 261-, which bias the first and second brake pistons 15□, 152 in the first and second brake hydraulic chambers 171-172, respectively, in the backward direction, that is, downwardly
262 are respectively housed, with the second return spring 26
The set load of 2 is set to 7 smaller than that of the first return spring 2.61. First brake piston 1-5. A piston rod 15 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 151.
A circlip-shaped stopper 27 that comes into contact with the top surface of the partition wall 16 is locked at the tip of □a. In addition, in order to restrict the retraction limit of the second brake piston 152, it is necessary to
A circlip-shaped stopper 28 that comes into contact with the upper end surface of the piston 9 is engaged with the piston rod 152a of the piston 152.

The second return spring 262 is located between a fixed seat plate 30 fixed to the upper end of the second brake piston 152 with a bolt 29 and a movable seat plate 31 that can slide on the bolt 29 within a limited stroke range. When the movable seat plate 31 is at its maximum distance from the fixed seat plate 30, both brake pistons 15
．． , 152 are at the retraction limit, they substantially abut against the lower end of the first brake piston 151.

The first and second brake pistons 151.15□ have piston cups 32.15 on each front side. ．． 322, respectively, and the middle part is made small in diameter, and a replenishment oil chamber 33. ．． 33
These oil chambers 331 and 332 are formed as piston cups 32! .

Oil supply hole 34 connected to each back of 32□. ．． 34□ is each brake piston 15. , 15□.

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. ,15□
When the piston cups 32 are located at the retraction limit,
．． ．． Immediately before 322, the first and second brake hydraulic chambers 17. ．． 172
Relief ports (relief ports) 371.312 and
Supply ports 38+ and 3B□, which are always open to the supply oil chambers 331 and 332, communicate 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 40 having a piston cup 41 on the front surface is slidably fitted into the cylinder hole 39. 1st
It is made to face the tip of the piston rod 151α of the brake piston 15.

The control piston 40 partitions the inside of the second cylinder hole 39 into a control hydraulic chamber 42 at the front and a replenishment oil chamber 43 at the rear, and abuts against the partition wall 16 by a return spring 44 contracted in the control hydraulic chamber 42. It is normally held at the retraction limit. The replenishment oil chamber 43 is the same as the replenishment oil chamber 33. ．． Similarly to 33□, the control piston 40 is provided with an oil supply hole 45 that communicates with the reservoir R via the oil passage 35 and communicates the chamber 43 with the back surface of the piston cup 41. In addition, 46 and 47 in FIG. 4 are air feeders.

The anti-lock device At controls the control piston 40, the normally closed electromagnetic control valve 48 and the normally open electromagnetic control valve 49 of -4j, and stores the hydraulic pressure of the control piston 40. It is composed of a pressure accumulator 4C and a hydraulic pump P that supplies pressure oil to the pressure accumulator ΔC. The normally closed type control valve 48 connects the hydraulic pump P and the pressure accumulator ACL with the control hydraulic chamber 42, and the normally open type control valve 49 connects the reservoir R and the control hydraulic chamber 42. The oil passages 51 are respectively interposed. In FIG. 3, reference numerals 52.53 and 54 are oil filters provided before and after the control valves 48 and 49, and 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 as shown in FIG. The one that is biased toward the front of the vehicle, in the illustrated example, is located behind the right engine block Eb, and thereby both engine blocks Ea.

Based on the deviation ε of Eb in the vehicle longitudinal direction (the dead space Dg behind the right engine block Eh is effectively used for installing the hydraulic pump P).

As shown in FIGS. 5 and 6, one end of a valve drive camshaft 60 is rotatably supported by a bearing 66 on the side wall of the engine body 61 of the engine block E6, and the hydraulic pump P is rotated by the valve drive camshaft 60. 8 Engine body 61 to be driven
mounted on.

The interior of the pump body 70 of the hydraulic pump P is divided from above into a spring chamber 75, a pump chamber 76, and an operating chamber 77 by a pair of upper and lower partition walls 73 and 71. In the working chamber 77,
A tip end of a relatively small diameter pump drive shaft 71 whose base end is fixed to the outer end of the valve drive camshaft 60 is provided. The tip thereof is formed into an eccentric pin 71α, into which a rolling bearing serving as the eccentric cam 72 is fitted. The plunger 79 is configured in two parts, including a large-diameter shaft portion T8α and a small-diameter shaft portion 78h formed sufficiently small in diameter compared to the diameter of the large-diameter shaft portion T8α, and the lower end of the small-diameter shaft portion 78h engages with the outer circumferential surface of the eccentric cam 72. do. The small diameter shaft portion 78h slidably passes through the partition wall 74 to open the pump chamber 7.
6 and comes into contact with the lower end of a large diameter shaft portion 78α that slidably passes through the partition wall 73. A movable seat plate 80 and a fixed seat plate 81 are attached to the upper end of the large-diameter shaft portion 78α protruding into the spring chamber 75 and the ceiling wall of the spring chamber 75, respectively, and a spring 82 is attached between these seat plates 80 and 81. It is contracted by applying a certain 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 oil passages 83 and 84 that communicate between the spring chamber 7-5 and the pump chamber 76, and the oil passage 84 is provided with the spring chamber 75.
A one-way valve, ie, a suction valve 86, is provided that allows fluid to flow in only one direction from the pump chamber T6 to the pump chamber T6.
A one-way valve, ie, a discharge valve 88, that allows fluid to flow in only one direction from the pump chamber 76 to the pressure accumulator Ac is provided in the flow path within the joint 87 that connects the pump chamber 76 and the oil path 50.

Further, the partition wall 73 is provided with an 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. ing.

Furthermore, the three oil passages 83.8 are provided in the pump body 70.
A filter chamber 89 is formed for merging the 4. An oil filter 9.0 is inserted, and this oil filter 90 is held by a cap 91 that closes the opening of the filter chamber 89. Therefore, the suction valve 8
6 can always send the hydraulic oil filtered by the oil filter 90 to the pump chamber 76. Also, cap 91
By removing the oil filter 90, the oil filter 90 can be easily replaced, and the pump chamber 7 can be opened by artificially opening the suction valve 86.
It is also possible to bleed air in step 6. In addition, 92 in Figure 6
is the drain bolt of the working chamber 77.

The pump body 70 has an annular positioning protrusion 70α integrally formed on one side that concentrically surrounds the pump drive shaft 71, and this protrusion 70a accommodates the oil seal 62 at the outer end of the valve drive camshaft 60. It is fitted into a seal nozzle 63 formed on the engine body 61 for this purpose. The convex portion 70a also serves to transmit and support the reaction force of the eccentric cam T2 applied to the pump body 70 to the engine body 61. After the positioning convex portion 70α is fitted, the pump body 70 is fixed to the engine body 61 with bolts 93 with its upper end, that is, the spring chamber 76 side tilted toward the center of the engine E, as shown in FIG. . Thereby, the hydraulic pump P can be hidden behind the engine block Eb, 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 95a at its inner end.

An inward flange 95b is integrally provided at the outer end, and the outward flange 95a is fitted into the seal housing 63 as an alignment member that holds the seal retainer 95 concentrically with the pump drive shaft 71, and is fitted into the seal housing 63 and has a positioning convex portion. It is held between 70α and the oil seal 62. The inward flange 95A is
It is disposed between the biased Cr cam 72 and the oil seal 96 as a retaining member for leaving the seal retainer 95 on the pump drive shaft 711jlII when the pump body 10 is removed.

Therefore, since the oil seals 62 and 96 are always held on the valve drive camshaft 60 and the pump drive shaft 71 by the seal retainer 95, it is possible that the oil seals 62 and 96 may come off and be damaged when the pump body 700 is attached or detached. will not be leaked to the 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 against the oil seal 96 during rotation is kept low (reduced).
The oil seal 96 has good durability and can prevent the hydraulic oil in the working chamber 77 from leaking over a long period of time.

Furthermore, when installing the hydraulic pump P, as shown in FIG. The phase curve on the circumference is made thicker (shifted) for each engagement position with the exhaust rocker arm 65. By doing this, the load applied to the valve drive camshaft 60 and the bearing 66 that supports it is distributed. 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 operated by the brake cylinder 1, the hydraulic pressure generated in the hydraulic chamber 9 is transferred from the input port 25 to the rear mask cylinder Mr via the oil passage 11. The hydraulic pressure is input to the hydraulic chamber 24, and the second brake piston 15□ is pushed in the forward direction, and the reaction force is supported by the sleeve 19 and is not transmitted to the bushing rod 20.

Further, when the brake pedal 2 is depressed, the pedal force is mechanically input to the second brake piston 152 via the bushing rod 20, and thereby the second brake piston 15□
is pushed in the forward direction.

Along with this, the hydraulic pressure in the reservoir 12 of the front mask cylinder Mf is 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, when the brake lever 1 and the brake pedal 2 are operated simultaneously, the front mask cylinder A1 f
The phase of the pressing force due to the output oil pressure and the pressing force due to the bushing rod 20 is applied to the second brake piston 152 as a braking input.

Then, when the second brake piston 15□ receives the brake input as described above, the first and second brake pistons 15s,
152 are first and second return springs 26;

26□ and moves forward while compressing them, and after those piston cups 321-322 pass the relief bows) 371+372, each brake piston y15. ．． 152, the first and second brake hydraulic chambers 17□.

172 , the hydraulic pressure generated in the first brake hydraulic chamber 17 is transmitted from the first output port 18 □ to the front wheel brake Bf via the oil path 4 to operate it, and the hydraulic pressure generated in the first brake hydraulic chamber 17 The hydraulic pressure generated is transmitted from the coil 2 output port 182 through the oil passage 5 to the rear wheel brake BR, which operates the front and rear wheels mf.

A braking force is applied to each Wr.

By the way, as mentioned above, the set load of the second return spring 2620 is set to be smaller than that of the first return spring 261, so when the second brake piston 152 first moves, the second return spring 2620 262 is compressed and hydraulic pressure is first generated in the second hydraulic pressure chamber 172. Then, after the oil pressure reaches a certain value fI P s, the first return spring 261 is compressed and the first brake piston 15□
begins to move forward, and hydraulic pressure is generated in the first brake hydraulic chamber 171.

Furthermore, since a known proportional pressure reducing valve V is provided in the oil passage 5 between the output port 182 of the second brake hydraulic pressure chamber 172 and the rear wheel brake 81, the output hydraulic pressure of the second output boat 182 is equal to or higher than the predetermined value 22. , the output hydraulic pressure is reduced at a constant ratio by the action of the proportional pressure reducing valve V, and the rear wheel brake B is
transmitted to r. On the other hand, the first brake hydraulic chamber 17. Since the output port 18□ and the oil passage 4 of the front wheel brake pedal are always in a conductive state, the output hydraulic pressure of the xl output port 18□ is directly transmitted to the front wheel brake Bf. As a result, the brake oil pressures of the front and rear wheel brakes Bf and BT increase along the brake oil pressure distribution A shown in FIG.

This characteristic approximates the ideal braking oil pressure distribution curve H of a motorcycle, and allows the operator to easily perform efficient braking.

11i When the lth brake piston 151 moves forward,
(Although the control piston 40 is also advanced via the piston rod 151α, normally the control hydraulic chamber 42 is communicated with the reservoir H via the normally open type control valve 49. The hydraulic oil is discharged to the reservoir R side as the control piston 40 moves forward, and hardly acts as a resistance to braking input.

If the front wheel If tries to lock due to braking, the signal processing device C shown in FIG. A close signal is sent to the normally open control valve 49 of the
Sends a valve opening signal to 8.

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 50 is made conductive, so that pressure oil flows from the pressure accumulator Ac through the oil passage 50 to the control hydraulic chamber 42. The hydraulic pressure causes the control piston 40 to slightly retract the first brake piston 15° against the braking input, thereby reducing the pressure in the first brake hydraulic chamber 171. As a result, the braking force of the front wheel brake Bf is reduced, and the locking phenomenon of the front wheel Wf is avoided.

Then, the signal processing device C detects the situation and returns both control valves 48 and 49 to their normal positions, thereby reducing the pressure in the brake hydraulic chamber 42. As a result, the braking force of the front wheel brake Bf increases again, and as the above operation is repeated at high speed, the front wheel Wf is efficiently (braked) without causing locking.

a first brake piston 15 by actuation of a control piston 40;
Conversely, the retreat of the rear wheel brake Bγ causes an increase in the pressure in the second brake hydraulic chamber 172, but since the increase in pressure is instantaneous, the rear wheel brake Bγ
This is absorbed by the elastic deformation of each part of the hydraulic system, so that the operating sensation of the brake lever 1 and brake pedal 2 is not impaired.

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 Wf and rear wheel Wr, the first. Second
The elastic force of the return springs 261-2620 causes the first. The second brake piston 1,51.152 moves back, and the first brake piston 1,51.152 moves back.
When the pressure inside the second brake hydraulic chambers 171 and 172 is reduced to below the arrow pressure, the atmospheric pressure is lowered to the replenishment oil chamber 33. ．． 332, the outer periphery of the piston cup 321. 172 to provide a gap between the inner wall of the first cylinder hole 14 and the replenishment oil chamber 331 .

332 to oil supply hole 341. 342? ! l' through each brake hydraulic chamber 17. , 172, and the surplus oil is sent to the oil line 35 from each IJ reef boat 37□, 37□.
, the force is returned to the reservoir R. During this time, each replenishment oil chamber 33. , 33□ is connected to supply port 3 by oil passage 36.
Oil is supplied through B+ and -38□.

On the other hand, even when the control piston 4o retreats, oil is supplied from the replenishment oil chamber 43 to the control hydraulic chamber 42 through the oil supply hole 45 by the same action as described above. Therefore, in particular, by reciprocating the control piston 4o, the control hydraulic chamber 42, oil passage 51, reservoir R1 oil passage 35, replenishment oil chamber 43, oil supply hole 4
5. Since oil circulation occurs in the path of the control hydraulic chamber 42, it is possible to prevent air bubbles from remaining in the control hydraulic circuit including the control hydraulic chamber 42.

Next is the action of the hydraulic pump P. In FIGS. 5 and 6, when the valve train camshaft 60, and therefore the pump drive shaft 71, rotates due to the operation of the engine E, the eccentric cam 72, which moves eccentrically, is moved by the spring 82. Give vertical reciprocating motion to the plunger 79 in cooperation with . Due to these reciprocating movements, the volume of the pump chamber 76 repeats expansion and contraction, and at the end of the expansion (C), the suction valve 86 is opened due to the reduced pressure in the pump chamber 76 (so that the pump chamber 76 is supplied from the reservoir R to the spring chamber 75. The oil is sucked into the pump chamber 76, and at the time of withdrawal 1.1, the discharge valve 88 is opened due to the increased pressure in the pump chamber 76, and pressurized oil is supplied from the pump chamber 76 to the pressure accumulator Ac. Make the plunger 79 reciprocate. During the eccentric movement of the eccentric cam 72, the outer race 72.Z of the eccentric cam 12 receives the elastic force of the spring 82 via the plunger 79, so it hardly rotates, and therefore the plunger 19 small diameter shaft part 7
fJb and outer race 7? By suppressing the sliding movement between the two as much as possible, it is possible to prevent wear of the engaging portion between the two. When the oil pressure in the pressure accumulator Ac rises and reaches a certain value, the pump chamber 7
The oil pressure in 6 shows a similar value, and the plunge of that oil pressure
Five of seventy-nine...'? ￥, 1lIllll ft1t 7
B+1 is χ, 11 i1 River 11 Getsu Gaba J^82's pushing force, that is, the set load is balanced to hold the large diameter shaft portion 78a near the upper limit of the rise by the small diameter shaft portion 78A, and the small diameter shaft Section 78
Only A repeats the vertical movement following the movement of the eccentric cam 72. In this case, the pushing force of the small diameter shaft portion 78b is applied to the pump chamber 76.
Since the suction valve 86 is supplied from the hydraulic pressure within the pump chamber 76, the suction valve 86 is maintained in a closed state by the hydraulic pressure within the pump chamber 76 even when the small diameter shaft portion 78b 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 is applied to the engagement surface between the small diameter shaft portion γ8h and the eccentric cam 72. However, since the diameter of the small-diameter shaft portion 78b 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 plunger is slidably provided in the pump body, and one end of the plunger is provided with the pump drive shaft V.
) 1 pump inside the main body 11I+
1. A spring is provided to bias the cam toward the outer circumferential surface, and the eccentric cam is configured with a rolling bearing fitted to an eccentric pin protruding from the end surface of the pump drive shaft, so a ready-made rolling bearing can be used as the eccentric cam. It becomes possible to use
Its configuration can be simplified. The outer race of the eccentric cam hardly rotates during the eccentric operation in which the plunger is reciprocated because it receives the elastic force of the spring via the plunger (therefore, there is no gap between the plunger and the outer race).
) N movement is suppressed as much as possible to prevent wear of the engaging parts of both,
Their durability can be improved. Furthermore, the driving torque required for reciprocating the plunger can be reduced.

[Brief explanation of drawings]

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 side view of the rear mask cylinder in the braking device, FIG. 5 is an enlarged longitudinal rear view of the hydraulic pump in the braking device when it is attached to the engine, and FIG. FIG. 7 is a sectional view taken along the line Vl-Vl in the figure, and FIG. 7 is a characteristic diagram of the braking oil pressure distribution ratio of the front and rear wheel brakes, in which line A shows the characteristic due to the braking device, and line B shows the ideal characteristic. . P...Hydraulic pump, 70...Pump body, 71...
・Pump drive shaft, 71a... Eccentric pin, T2... Eccentric cam, 79... Plunger, 82... Spring Patent applicant Honda Motor Co., Ltd.

Claims (1)

[Claims] A plunger is slidably provided within the pump body, one end of the plunger is engaged with the outer circumference of an eccentric cam provided on the pump drive shaft, and the plunger is disposed within the pump body on the outer circumference of the eccentric cam. 1. A hydraulic pump, wherein a spring is disposed to bias the eccentric cam toward the pump, and the eccentric cam is configured by a rolling bearing fitted into an eccentric pin protruding from an end surface of the pump drive shaft.