Axial inclined disc type hydraulic planger pump
Technical field
The present invention relates to axial inclined disc type hydraulic planger pump.
Background technique
Plunger pump working principle, plunger pump are a kind of of reciprocating pump, belong to volume pump, and its plunger drives by the eccentric rotary of pump shaft, to-and-fro motion, and it sucks and expulsion valve all is one-way valve.When drawing outside the plunger, working room's internal pressure reduces, and outlet valve cuts out, and when being lower than inlet pressure, inlet valve is opened, and liquid enters; When pushing away in the plunger, working room's pressure raises, and inlet valve cuts out, and when being higher than outlet pressure, outlet valve is opened, and liquid is discharged.
Axial piston pump with the piston shoes structure is present most popular axial piston pump, and the plunger that is placed in the cylinder body contacts with swash plate by piston shoes, and when transmission shaft drove the cylinder body rotation, swash plate was pulled out plunger or pushed back from cylinder body, finishes suction oil process.Fluid in the work cavity volume that plunger and cylinder hole form communicates with suction, the oil-discharging cavity of pump respectively by oil distribution casing.Stroking mechanism is used for changing the inclination angle of swash plate, can change pump delivery by the inclination angle of regulating swash plate.But it is poor that existing plunger pump pressure is regulated receptance, is difficult to proof load and changes the oil mass that can regulate in real time oil pump.
Summary of the invention
The purpose of this invention is to provide a kind of axial inclined disc type hydraulic planger pump, because flow piston large end face is long-pending greater than the small end area, realize that thus pressure increases, flow reduces, and realizes variable displacement with constant power, otherwise when load reduces, the pressure at flow piston two ends reduces thereupon, the decrement when this moment, the power spring also maintained high pressure, and the hydraulic coupling of the large end of flow piston reduces, flow increases, and control mode is reasonable.
Technological scheme of the present invention is as follows:
Axial inclined disc type hydraulic planger pump, include the double step thrust piston, the a mouth of double step thrust piston, before the b mouth is connected respectively to, on the rear pump, the plunger end face overhead of double step thrust piston is in the adjustment (adjusting) lever end face, be set with the power spring on the adjustment (adjusting) lever, the rear side pressure of power spring is equipped with spring seat, the spool that is equipped with power control valve is pressed in the end of adjustment (adjusting) lever, spool is provided with step, power control valve has two hydraulic fluid port d mouths, the c mouth, spring seat is fixedly connected with the flow piston, the little distolateral valve pocket of flow piston and a mouth of double step thrust piston, the c mouth of power control valve connects, the c mouth of the valve pocket power control valve that the flow piston is distolateral greatly connects, and the flow piston is fixedly connected with the swash plate of plunger pump.
The rear end of described adjustment (adjusting) lever is fixed with fixed base, presses between fixed base and the spring seat and is putting the power spring.
Control mode of the present invention is reasonable, and pressure is regulated receptance and improved, and guaranteed the oil mass that load variations can be regulated oil pump in real time, thereby the pressure of oil circuit control is big or small, has effectively guaranteed the usability of load sensitive pump.
Description of drawings
Fig. 1 is structural representation of the present invention.
Fig. 2 is the connection diagram between double step thrust piston and the power control valve.
Embodiment
Referring to accompanying drawing, axial inclined disc type hydraulic planger pump, include double step thrust piston 1, the a mouth of double step thrust piston 1, before the b mouth is connected respectively to, on the rear pump, the plunger end face overhead of double step thrust piston 1 is in adjustment (adjusting) lever 2 end faces, be set with power spring 3 on the adjustment (adjusting) lever 2, the rear side pressure of power spring 3 is equipped with spring seat 4, the spool 6 that is equipped with power control valve 5 is pressed in the end of adjustment (adjusting) lever 2, spool 6 is provided with step, power control valve 5 has two hydraulic fluid port d mouths, the c mouth, spring seat is fixedly connected with flow piston 7, flow piston 7 little distolateral valve pockets and a mouth of double step thrust piston, the c mouth of power control valve connects, the c mouth of the valve pocket power control valve that the flow piston is distolateral greatly connects, flow piston 7 is fixedly connected with the swash plate of plunger pump 8, and the rear end of adjustment (adjusting) lever is fixed with fixed base 9, presses between fixed base 9 and the spring seat and is putting power spring 3.
The thrust piston of double step of the present invention, a mouth connect the pressure oil of another pump (rear pump) of duplex plunger pump, and the b mouth connects the pressure oil of this pump (front pump), and the front and back pump respectively draws a road binders to thrust piston, realize the control of double pump intersection.Increase along with induced pressure, a, the pressure of b two hydraulic fluid ports is also along with increase, thrust piston promotes adjustment (adjusting) lever compression horsepower spring and promotes spool, d mouth and e mouth disconnected when the power spring-compressed arrived to a certain degree, d mouth and c mouth are connected, at this moment the large end of flow piston just begins oil-feed, because ' power=pressure * active area ' flow piston pressure at two ends is identical, large end face is long-pending greater than the small end area, so the flow piston can be moved to the left (flow reduces) under the effect of hydraulic coupling, the flow piston is moved to the left and drives the further compression horsepower spring of shifting block promotion spring seat, make thrust piston and adjustment (adjusting) lever all left, spool also is moved to the left thereupon, and c mouth and d mouth disconnect, the large end fuel cut-off of flow piston, the flow piston stops mobile, realizes that thus pressure increases, and flow reduces, make: pressure * flow=steady state value, realize variable displacement with constant power.Otherwise when load reduces, the pressure at flow piston two ends reduces thereupon, decrement when this moment, the power spring also maintained high pressure, the hydraulic coupling of the large end of flow piston reduces, be that spring force is greater than the hydraulic coupling of the large end of flow piston, the power spring just promote shifting block drive the flow piston to the right (large end) mobile, flow increases.