WO2022016449A1 - 止回阀和中央阀 - Google Patents

止回阀和中央阀 Download PDF

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Publication number
WO2022016449A1
WO2022016449A1 PCT/CN2020/103783 CN2020103783W WO2022016449A1 WO 2022016449 A1 WO2022016449 A1 WO 2022016449A1 CN 2020103783 W CN2020103783 W CN 2020103783W WO 2022016449 A1 WO2022016449 A1 WO 2022016449A1
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WO
WIPO (PCT)
Prior art keywords
valve
groove
check valve
plate
check
Prior art date
Application number
PCT/CN2020/103783
Other languages
English (en)
French (fr)
Inventor
刘晓娜
Original Assignee
舍弗勒技术股份两合公司
刘晓娜
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 舍弗勒技术股份两合公司, 刘晓娜 filed Critical 舍弗勒技术股份两合公司
Priority to CN202080098564.7A priority Critical patent/CN115279996B/zh
Priority to PCT/CN2020/103783 priority patent/WO2022016449A1/zh
Publication of WO2022016449A1 publication Critical patent/WO2022016449A1/zh

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K11/00—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
    • F16K11/02—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit
    • F16K11/06—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements
    • F16K11/065—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members
    • F16K11/07—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members with cylindrical slides
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K15/00—Check valves
    • F16K15/14—Check valves with flexible valve members
    • F16K15/16—Check valves with flexible valve members with tongue-shaped laminae

Definitions

  • the present invention relates to camshaft phasers, and in particular to a central valve for controlling the flow of pressure medium of the camshaft phaser and a check valve disposed within the central valve.
  • variable valve timing system is an important part of ensuring the performance of the engine. It can adjust the opening and closing of the valve of the engine according to the needs, so that the engine can obtain the desired performance such as power output.
  • the variable valve timing system includes assembly with the camshaft. Camshaft phase adjusters together.
  • a camshaft phaser is usually constructed with at least two interacting pressure chambers (A chamber and B chamber) between which the camshaft phase can be adjusted or maintained by a pressure medium flowing between the two pressure chambers.
  • the above-mentioned flow of pressure medium eg oil
  • a control valve one type of control valve being a central valve placed in the central bore of the rotor of the camshaft phaser.
  • a central valve typically includes a piston, sleeve, check valve and housing.
  • the sleeve is sleeved outside the piston
  • the casing is sleeved outside the sleeve
  • the check valve is disposed between the sleeve and the casing.
  • a support plate is arranged between the sleeve and the housing, and the check valve is arranged on the support plate.
  • a partial area of the outer circumference of the sleeve needs to be provided with a special structure to match the check valve in the open state.
  • the central valve of the above structure includes a large number of parts and a complex structure, which makes the cost of the central valve high.
  • the support plate occupies the oil path between the sleeve and the casing, so that the oil flow becomes smaller, which is not conducive to the timely and effective response of the camshaft phase adjuster.
  • the purpose of the present invention is to overcome or at least alleviate the above-mentioned deficiencies of the prior art, and to provide a check valve and a central valve including the check valve.
  • a check valve for being arranged in a valve groove of a central valve of a camshaft phase adjuster to control the flow of pressure medium from a first pressure chamber of the camshaft phase adjuster outflow, through the valve slot to the second pressure chamber, or outflow from the second pressure chamber, through the valve slot to flow to the first pressure chamber, wherein,
  • the check valve includes a main plate, a back plate and two valve plates,
  • the valve plate is partially connected to the main plate, so that the valve plate can change its position relative to the main plate under the action of the pressure of the pressure medium, so as to have a closed state and a fully open state,
  • the backing plate provides support for the valve plate when the valve plate is in a fully punched state.
  • the backing plate includes two stops at which the backing plate provides support for the valve plate in a fully open state
  • the stopper portion is disposed obliquely with respect to the main board, and the closer to the connection portion between the valve plate and the main board, the smaller the distance between the stopper portion and the main board.
  • a first port of a check valve and a second port of a check valve are provided on the back plate, and the first port of the check valve enables the pressure medium to axially flow in the valve groove.
  • the second port of the check valve enables the pressure medium in the valve groove to flow out of the valve groove.
  • the first port of the check valve and the second port of the check valve communicate with each other to form a check valve port in the form of a single hole.
  • the size of at least a partial area of the backing plate is smaller than the size of the valve groove, so that the pressure medium can flow axially in the valve groove, And the pressure medium in the valve groove can flow out of the valve groove.
  • the check valve is formed by stamping and bending a sheet of material.
  • the check valve is formed as a ring or half ring.
  • the valve plate includes a valve head and a valve tail, and the valve tail is connected to the valve head and the main board,
  • the size of the valve head is larger than the size of the valve tail.
  • valve heads of the two valve sheets of the check valve are opposite to each other, and the valve tails are arranged opposite to each other.
  • a central valve for a camshaft phaser and for controlling the flow of pressure medium within the camshaft phaser, wherein,
  • the central valve comprises a sleeve, a housing and a check valve according to the present invention, the housing is sleeved outside the sleeve,
  • the peripheral wall of the casing is provided with at least one group of oil inlet holes, each group of oil inlet holes includes a first oil inlet hole and a second oil inlet hole, and the first oil inlet hole is used for connecting with the first oil inlet hole.
  • the pressure chamber is communicated, and the second oil inlet hole is used to communicate with the second pressure chamber,
  • the outer peripheral wall of the sleeve is partially recessed radially inward to form at least one valve groove, the check valve is arranged in the valve groove, and the two valve plates of the check valve are respectively located in the
  • the first oil inlet hole and the second oil inlet hole are used to control the opening and closing of the first oil inlet hole and the second oil inlet hole.
  • the valve groove in the axial direction of the sleeve, has an open first end and a closed second end, and the pressure medium can flow into the valve groove from the first end.
  • the first end of the valve slot is connected to an inlet slot
  • the size of the inlet groove is smaller than the size of the valve groove in the circumferential direction of the sleeve.
  • a sleeve oil inlet is provided at the bottom of the valve groove on the radially inner side of the central valve, and the pressure medium can flow out of the valve groove from the sleeve oil inlet, and
  • the sleeve oil inlet is at least partially shielded by the backing plate.
  • valve plate when the valve plate is in a closed state, the surface of the valve plate facing the casing is completely abutted with the inner peripheral wall of the casing.
  • the number of the check valves is greater than one, and the number of the valve slots is greater than or equal to the number of the check valves.
  • the check valve according to the present invention has a simple structure and is convenient to manufacture.
  • the central valve according to the invention has the same advantages.
  • FIG. 1 is a schematic view of the oil inlet of the central valve according to the first embodiment of the present invention in a cutaway state.
  • FIG 2 is an exploded view of a partial structure of the center valve according to the first embodiment of the present invention.
  • FIG. 3 is a schematic structural diagram of the check valve according to the first embodiment of the present invention.
  • FIG. 4 is a schematic diagram of the oil drain from the A chamber and the oil intake from the B chamber under the cutaway state of the central valve according to the first embodiment of the present invention.
  • FIG. 5 is a schematic structural diagram of a check valve according to a second embodiment of the present invention.
  • FIG. 6 is a schematic structural diagram of a check valve according to a third embodiment of the present invention.
  • FIG. 7 is a schematic structural diagram of a check valve according to a fourth embodiment of the present invention.
  • FIG. 8 is a schematic structural diagram of a check valve according to a fifth embodiment of the present invention.
  • 40 check valve 41 valve plate; 411 valve head; 412 valve tail; 42 main board; 43 back plate; 431 stop part; 40a check valve first port; 40b check valve second port; 40k check valve oil mouth;
  • AX represents the axial direction of the central valve, which is consistent with the axial direction of the piston 10;
  • R represents the radial direction of the central valve, and the radial direction R is consistent with the radial direction of the piston 10. .
  • the central valve includes a piston 10 , a sleeve 20 , a housing 30 , a check valve 40 and a spring 50 .
  • the piston 10 , the sleeve 20 and the casing 30 are all hollow cylinders, the sleeve 20 is sleeved outside the piston 10 , and the casing 30 is sleeved outside the sleeve 20 .
  • the piston 10 can reciprocate relative to the sleeve 20 in the axial direction AX, and a spring 50 that can expand and contract in the axial direction AX is provided between the piston 10 and the sleeve 20 .
  • the casing 30 is penetrating in the axial direction AX, and one end in the axial direction AX (the right end in the figure, hereinafter the end on the right side of each component in FIG. 1 is referred to as the first end) is a pressure medium (such as oil). ) of the input port P, for example, oil can be pumped to the input port P by an oil pump and the oil can flow into the interior of the housing 30 in a controlled manner (ie into the central valve).
  • a pressure medium such as oil
  • the casing 30 is provided with at least one group of oil outlet holes and at least one group of oil inlet holes in the circumferential direction, and each group of oil outlet holes includes a first oil outlet hole 301 and a second oil outlet hole arranged along the axial direction AX.
  • Each group of oil inlet holes includes a first oil inlet hole 311 and a second oil inlet hole 312 arranged along the axial direction AX.
  • the first oil outlet hole 301 and the first oil inlet hole 311 are both communicated with the first pressure chamber (hereinafter also referred to as the A chamber) of the camshaft phase adjuster, and the second oil outlet hole 302 and the second oil inlet hole 312 are both connected to the cam.
  • the second pressure chamber (hereinafter also referred to as the B chamber) of the shaft phase adjuster communicates with each other.
  • the sleeve 20 will be described with reference to FIGS. 2 and 4 .
  • the sleeve 20 is fixed to the housing 30 in the axial direction AX.
  • the end of the sleeve 20 facing the input port P (the first end of the sleeve 20 ) is closed.
  • the outer peripheral wall of the sleeve is recessed radially inward to form at least one valve groove 21 and at least one set of oil grooves.
  • the first end of the valve groove 21 is open in the axial direction AX and is connected to the inlet groove 21a, and the oil flowing in from the input port P can flow to the valve groove 21 through the inlet groove 21a.
  • the size of the inlet groove 21a is smaller than that of the valve groove 21, so at the first end of the valve groove 21, the inlet groove 21a partially protrudes on both sides of the valve groove 21 in the circumferential direction, the two The protruding structure can play a role in positioning the check valve 40 installed in the valve groove 21 to be described later in the axial direction AX.
  • valve groove 21 The second end (the left end in FIG. 1 ) of the valve groove 21 is closed.
  • a sleeve oil inlet port 20a penetrating in the radial direction R is opened in the bottom portion of the valve groove 21 (the inner part in the radial direction R) in a substantially middle region in the axial direction AX of the valve groove 21 .
  • the oil in the valve groove 21 can flow between the sleeve 20 and the piston 10 through the sleeve oil inlet 20a.
  • Each group of oil grooves includes a first chamber oil groove 22 and a second chamber oil groove 23 arranged along the axial direction AX.
  • the first chamber oil groove 22 is closer to the input port P than the second chamber oil groove 23.
  • the bottom of the first chamber oil groove 22 (the inner part in the radial direction R) is provided with a diameter in the area close to the input port P in the axial direction AX.
  • the first chamber oil outlet 22a penetrating toward R, and the bottom of the second chamber oil groove 23 (the inner part in the radial direction R) are opened in the region far from the input port P in the axial direction AX, and the bottom portion (the inner part in the radial direction R) of the oil groove 23 is provided with a penetration in the radial direction R.
  • the second chamber oil outlet 23a The oil between the sleeve 20 and the piston 10 can flow to the first chamber oil groove 22 through the first chamber oil outlet 22a, and to the second chamber oil groove 23 through the second chamber oil outlet 23a.
  • the first oil outlet hole 301 on the housing 30 is at least partially (preferably completely) communicated with the first chamber oil groove 22, and the second oil outlet hole 302 is at least partially (preferably completely) communicated with the second chamber oil groove 23; Both the first oil inlet hole 311 and the second oil inlet hole 312 are at least partially (preferably completely) in communication with the valve groove 21 (without considering the check valve 40).
  • the check valve 40 is installed in the valve groove 21. With the change of the oil pressure in the A cavity and the B cavity, the two valve plates on the check valve 40 will be selectively opened, so that the oil in the A cavity or the B cavity is opened. Oil flows into the valve groove 21 .
  • the check valve 40 includes a main plate 42 , a back plate 43 and two valve plates 41 .
  • the main plate 42 is roughly in the shape of a hollowed strip, and the two valve plates 41 are partially connected to the main plate 42, so that the two valve plates 41 can move relative to the main plate 42.
  • the back plate 43 is connected to the main plate 42 and can provide support for the valve plate 41 in the opening direction of the valve plate 41 , preventing the valve plate 41 from being easily damaged or failing due to an excessively large opening angle.
  • the check valve 40 has a substantially trapezoidal annular shape.
  • the lower bottom of the trapezoidal ring (the longer trapezoidal bottom on the upper layer in FIG. 3 ) forms the main plate 42 of the check valve 40 , and the upper bottom and the oblique side of the trapezoidal ring (the part on the lower layer in FIG. 3 ) constitute the back plate 43 .
  • the check valve 40 is formed by stamping and bending a sheet material (eg, a steel sheet). It should be understood that the check valve 40, which is bent to form a generally annular shape, may leave a partial gap where the bent sheets meet end to end, such as the rightmost gap in FIG. 3, however this is not required and the present The invention does not limit the position of the slit.
  • a sheet material eg, a steel sheet.
  • the valve plate 41 is located in the middle of the main plate 42, or the main plate 42 surrounds the valve plate 41; more precisely, in this embodiment, the valve plate 41 is formed by cutting a strip-shaped plate, and the valve plate 41 is pressed in the middle of the plate.
  • the shape cuts out grooves or slits, the ends of the grooves or slits are not connected, the part surrounded by the contour of the groove or the slit forms the valve plate 41 , and the peripheral part of the groove or the slit forms the main plate 42 .
  • the uncut part between the head and tail of the slot or slot forms the connection part between the valve plate 41 and the main board 42 .
  • the circumferential direction of the sleeve 20 (or the direction tangential to the circumferential direction) is defined as the width direction of the valve groove 21 and the check valve 40
  • the axial direction AX of the sleeve 20 is defined as the longitudinal direction of the valve groove 21 and the check valve 40
  • the radial direction R of the sleeve 20 is defined as the depth direction of the valve groove 21 and the check valve 40 .
  • the width of the check valve 40 is approximately the same as the width W of the valve groove 21
  • the length of the check valve 40 is approximately the same as the length L of the valve groove 21
  • the depth of the check valve 40 is greater than or equal to the depth of the valve groove 21 (
  • the check valve 40 can be adapted to the depth of the valve groove 21 in a manner of being slightly compressed in the depth direction). Thereby, the check valve 40 can be just disposed in the valve groove 21 and positioned by the valve groove 21 .
  • the valve plate 41 is elongated, and includes a valve head 411 and a valve tail 412 , and the valve tail 412 is connected to the valve head 411 and the main board 42 .
  • the valve heads 411 of the two valve plates 41 are opposite to each other, and the valve tails 412 are opposite to each other.
  • the width of the valve head 411 is greater than the width of the valve tail 412 .
  • the side of the valve plate 41 close to the back plate 43 (that is, when the check valve 40 is installed in the valve groove 21 , the radially inner side of the valve plate 41 ) is defined as the inner side of the valve plate 41 , and the side of the valve plate 41 away from the valve plate 41 is defined.
  • One side of the back plate 43 ie, the radially outer side of the valve plate 41 when the check valve 40 is installed in the valve groove 21 ) is defined as the outer side of the valve plate 41 .
  • valve plate 41 When the oil pressures on both sides of the valve plate 41 are approximately equal, the valve plate 41 does not deviate from the plane where the main board 42 is located, also known as the valve plate 41 is in a closed state in this case; the oil pressure on the outside of the valve plate 41 is greater than that on the inside of the valve plate 41 In the case of pressure, the valve head 411 deviates from the plane of the main plate 42 and bends to the back plate 43 until the valve head 411 contacts the back plate 43, which is also called in this case the valve plate 41 is in a fully open state.
  • the shape of the back plate 43 is preferably such that when the valve plate 41 is in an open state, the back plate 43 can contact the valve plate 41 with a large area.
  • the above-mentioned preferred shape mainly includes two aspects, one is that the inclination angle of the back plate 43 relative to the main plate 42 is compatible with the inclination angle of the valve plate 41 in the fully open state;
  • the sheet 41 provides a sufficiently large and uniform blocking force.
  • the back plate 43 includes two stop parts 431 inclined relative to the main plate 42 , and the back plate 43 provides support for the valve plate 41 in a fully opened state at the stop parts 431 , and the stop parts
  • the inclination direction of the valve plate 431 is similar to the inclination direction of the opposite valve plate 41 in the open state. The above arrangement makes the valve plate 41 not easily damaged during frequent opening and closing switching.
  • the back plate 43 is also provided with a first port 40a of the check valve and a second port 40b of the check valve.
  • the first port 40a of the check valve prevents the oil from being blocked by the back plate 43 when it flows through the inlet groove 21a and enters the valve groove 21, or in other words enables the oil to flow axially in the valve groove 21;
  • the second port 40b ensures that the oil in the valve groove 21 will not be blocked by the back plate 43 during the process of flowing from the sleeve oil inlet 20a to the following cavity 11, or in other words, the pressure medium in the valve groove 21 can flow out of the valve Slot 21.
  • the second port 40b of the check valve is provided in approximately the middle of the back plate 43, and the first port 40a of the check valve is provided in the region of the back plate 43 close to the connection with the main board 42.
  • the main body of one of the two stoppers 431 is located between the first port 40a of the check valve and the second port 40b of the check valve.
  • valve plate 41 When the check valve 40 is installed in the valve groove 21 and the oil pressures on both sides of the valve plate 41 are substantially equal (the valve plate 41 is in a closed state), the two valve plates 41 are in close contact with the inner wall of the housing 30, and the two valve plates 41 are in close contact with the inner wall of the housing 30.
  • the valve heads 411 completely block the first oil inlet hole 311 and the second oil inlet hole 312 in the housing 30 respectively, so as to ensure the good check valve function of the check valve 40 .
  • the valve head 411 and the surface of the inner wall of the casing 30 around the oil inlet holes have the same curved shape; for example, the casing
  • the inner wall of 30 is a cylindrical surface.
  • the valve plate 41 and the main plate 42 are both curved surfaces and the curvature is the same as the above-mentioned cylindrical surface; for example, the valve plate of the check valve 40 41 and the main plate 42 are both flat, and in this case, the inner wall of the housing 30 is formed in a flat shape at least in the vicinity of the oil inlet hole (for example, by stamping).
  • valve plate 41 since the outer surface of the valve plate 41 is in close contact with the housing 30, the valve plate 41 cannot be opened radially outward, so that the first oil inlet hole 311 and the second oil inlet hole 312 can only supply oil into the valve grooves 21, The oil cannot flow out of the valve groove 21 .
  • a substantially central region of the outer circumference of the piston 10 is recessed inwardly to form an annular cavity 11 .
  • the length of the cavity 11 in the axial direction AX is such that during the axial movement of the piston 10 relative to the sleeve 20, the piston 10 has the following positions: (1) the cavity 11 is communicated with the oil inlet port 20a of the sleeve, and The concave cavity 11 communicates with the first cavity oil outlet 22a, (2) the concave cavity 11 communicates with the sleeve oil inlet 20a, and the concave cavity 11 communicates with the second cavity oil outlet 23a.
  • FIG. 1 shows the path of the oil flowing from the input port P into the cavity 11 .
  • FIG. 1 only shows the path for the oil to flow into the cavity 11 located at the upper part, and the path for the oil to flow into the cavity 11 located at the lower part is omitted.
  • the oil flowing from the input port P flows into the valve groove 21 through the inlet groove 21a, then flows through the first check valve port 40a and the second check valve port 40b of the check valve 40 in sequence, and then flows through the sleeve oil inlet port 20a into the cavity 11 .
  • the hollow arrows in Fig. 4 show the path of the oil drain from the A cavity and the oil intake from the B cavity.
  • the piston 10 moves to a position where the oil outlet 23a of the second cavity is at least partially communicated with the concave cavity 11 .
  • the oil flows out of the A cavity under the action of pressure.
  • the oil pressure on the outside of the valve plate 41 at the first oil inlet hole 311 is greater than the oil pressure on the inside, the valve plate 41 at the first oil inlet hole 311 is opened, and the oil flows into the valve groove 21 and flow through the second port 40b of the check valve into the cavity 11.
  • the oil in the cavity 11 flows into the second cavity oil groove 23 through the second cavity oil outlet 23a under the action of pressure, and the oil in the second cavity oil groove 23 flows into the B cavity through the second oil outlet hole 302 under the action of pressure.
  • the central valve according to the present invention can be provided with at least one check valve 40, and when conditions permit, the number of check valves 40 can also be appropriately increased to increase the flow speed of oil between the A cavity and the B cavity .
  • the central valve preferably includes two circumferentially spaced check valves 40 .
  • valve groove 21 is also the oil inlet groove of the central valve.
  • four valve grooves 21 can be set on the sleeve 20, two of which are provided with check valves 40 in the valve grooves 21.
  • the check valve 40 is not provided in the two valve grooves 21 .
  • the valve slot 21 provided with the check valve 40 can not only be used for the central valve to enter the oil, but also for the oil return of the A cavity or B cavity; the valve slot 21 without the check valve 40 is not used to control the return of the A cavity or the B cavity. Oil.
  • the portion of the peripheral wall of the housing 30 corresponding to the valve groove 21 without the check valve 40 is not provided with oil inlet holes and oil outlet holes (including the first oil outlet hole 301, the second oil outlet hole 302, the first oil outlet hole 302, the first oil outlet hole oil inlet hole 311 and second oil inlet hole 312).
  • FIG. 5 A check valve 40 according to a second embodiment of the present invention will be described with reference to FIG. 5 .
  • the second embodiment is a modification of the first embodiment, and descriptions of the same parts as those of the first embodiment are omitted. It should be understood that FIG. 5 only shows the general structure of the check valve 40 , and the two valve plates connected to the main plate 42 and the openings corresponding to the valve plates are not shown in FIG. 5 .
  • the main difference between this embodiment and the first embodiment is that the first port 40a of the check valve and the second port 40b of the check valve in the first embodiment are combined into a long check valve oil port 40k, That is, the solid part between the first port 40a of the original check valve and the second port 40b of the check valve is omitted, that is, at least one stopper 431 is formed by the back plate 43 on both sides in the width direction of the oil port 40k of the check valve. partially act.
  • FIG. 6 A check valve 40 according to a third embodiment of the present invention will be described with reference to FIG. 6 .
  • the third embodiment is a modification of the first embodiment, and descriptions of the same parts as those of the first embodiment are omitted. It should be understood that FIG. 6 only shows the general structure of the check valve 40 , and the two valve plates connected to the main plate 42 and the openings corresponding to the valve plates are not shown in FIG. 6 .
  • the main difference between this embodiment and the first embodiment is that the back plate 43 is divided into two spaced apart parts, each part forms a stopper part 431 , and each stopper part 431 is connected to the main plate 42 .
  • the spaced area between the two stoppers 431 forms the second port 40b of the check valve, and one of the stoppers 431 is provided with the first port 40a of the check valve.
  • FIG. 7 A check valve 40 according to a fourth embodiment of the present invention will be described with reference to FIG. 7 .
  • the fourth embodiment is a modification of the first embodiment, and descriptions of the same parts as those of the first embodiment are omitted. It should be understood that FIG. 7 only shows the general structure of the check valve 40 , and the two valve plates connected to the main plate 42 and the openings corresponding to the valve plates are not shown in FIG. 7 .
  • the back plate 43 is not provided with an opening. Instead, the width of at least part of the back plate 43 is smaller than the width W of the valve groove 21, so that the inlet groove 21a ( 2) the oil flowing into the valve groove 21 can flow axially through the valve groove 21 to the sleeve oil inlet 20a; .
  • the width of the middle most area of the back plate 43 is smaller than the dimension of the sleeve oil inlet 20a in the width direction.
  • FIG. 8 A check valve 40 according to a fifth embodiment of the present invention will be described with reference to FIG. 8 .
  • the fifth embodiment is a modification of the third embodiment and the fourth embodiment, and descriptions of the same parts as those of the above-described embodiments are omitted. It should be understood that FIG. 8 only shows the general structure of the check valve 40 , and the two valve plates connected to the main plate 42 and the openings corresponding to the valve plates are not shown in FIG. 8 .
  • the two stopper parts 431 are completely spaced apart, and each stopper part 431 is connected to the main plate 42 .
  • the spaced-apart area between the two stops 431 forms the second port 40b of the check valve.
  • the stopper portion 431 is not provided with an opening, and the oil flows into the valve slot 21 by passing through the gap between the stopper portion 431 and the side wall of the valve slot 21. Therefore, at least the stopper close to the inlet slot 21a (also refer to FIG. 2 ).
  • the width of at least a partial area of the blocking portion 431 is smaller than the width W of the valve groove 21 .
  • the present invention uses an integrated check valve 40 to control the flow of oil between the A cavity and the B cavity.
  • the check valve 40 has a simple structure and is convenient to manufacture, and does not require multiple components.
  • the sleeve 20 matched with the check valve 40 has a simple structure, strong versatility and low manufacturing cost.
  • valve groove 21 of the check valve 40 can simultaneously act as an oil inlet groove for oil entering the central valve, and the check valve 40 does not affect the amount of oil entering the central valve.
  • the stopper portion 431 When the stopper portion 431 can effectively support the valve head 411 in the fully opened state, the stopper portion 431 may be provided not inclined to the main plate 42 .
  • the two valve heads 411 on the check valve 40 may not be arranged opposite to each other.
  • the two valve heads 411 may also be arranged in the same direction or opposite to each other.

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  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
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Abstract

一种中央阀及其止回阀(40)，止回阀(40)用于设置在凸轮轴相位调节器的中央阀的阀槽(21)内，以控制压力介质从所述凸轮轴相位调节器的第一压力腔内流出、经由所述阀槽(21)而流至第二压力腔，或从所述第二压力腔内流出、经由所述阀槽(21)而流至所述第一压力腔，其中，所述止回阀包括主板(42)、背板(43)和两个阀片(41)，所述阀片(41)部分地与所述主板(42)相连，使得所述阀片(41)能在所述压力介质的压力作用下改变相对于所述主板(42)的位置，从而具有关闭状态和完全打开状态，所述背板(43)在所述阀片(41)处于完全打完状态时为所述阀片(41)提供支承。

Description

止回阀和中央阀 技术领域
本发明涉及凸轮轴相位调节器，且特别地涉及用于控制凸轮轴相位调节器的压力介质流动的中央阀和设置于中央阀内的止回阀。
背景技术
可变气门正时系统是保证发动机性能的重要组成部分，其能够根据需要而调节发动机的气门的开闭，从而使得发动机获得期望的动力输出等性能，可变气门正时系统包括与凸轮轴组装在一起的凸轮轴相位调节器。
凸轮轴相位调节器通常构造有至少两个相互作用的压力腔(A腔和B腔)，通过压力介质在两个压力腔之间流动可以调整或保持凸轮轴相对于曲轴的相位。压力介质(例如油)的上述流动通常需要借助控制阀实现，一种类型的控制阀为置于凸轮轴相位调节器的转子的中央孔内的中央阀。
中央阀通常包括活塞、套筒、止回阀和壳体。套筒套设在活塞外，壳体套设在套筒外，止回阀设置于套筒和壳体之间。为了方便止回阀的设置，有一种可能的方案是在套筒和壳体之间设置支承板，并将止回阀设置于支承板上。此外，为了限制止回阀的打开角度，套筒的外周的部分区域需要被设置成特殊的结构以与打开状态的止回阀相匹配。
然而，上述结构的中央阀包含零部件数量多且结构复杂，使得中央阀成本高。并且，支承板占用了套筒和壳体之间的油路，使得油的流量变小，不利于凸轮轴相位调节器的及时有效的响应。
发明内容
本发明的目的在于克服或至少减轻上述现有技术存在的不足，提供一种 止回阀和包括该止回阀的中央阀。
根据本发明的第一方面，提供一种止回阀，其用于设置在凸轮轴相位调节器的中央阀的阀槽内，以控制压力介质从所述凸轮轴相位调节器的第一压力腔内流出、经由所述阀槽而流至第二压力腔，或从所述第二压力腔内流出、经由所述阀槽而流至所述第一压力腔，其中，
所述止回阀包括主板、背板和两个阀片，
所述阀片部分地与所述主板相连，使得所述阀片能在所述压力介质的压力作用下改变相对于所述主板的位置，从而具有关闭状态和完全打开状态，
所述背板在所述阀片处于完全打完状态时为所述阀片提供支承。
在至少一个实施方式中，所述背板包括两个止挡部，所述背板在所述止挡部处为处于完全打开状态的所述阀片提供支承，
所述止挡部相对于所述主板倾斜地设置，越靠近所述阀片与所述主板的连接部，所述止挡部与所述主板之间间隔的距离越小。
在至少一个实施方式中，所述背板上设有止回阀第一口和止回阀第二口，所述止回阀第一口使得所述压力介质能在所述阀槽内轴向流动，所述止回阀第二口使得所述阀槽内的所述压力介质能流出所述阀槽。
在至少一个实施方式中，所述止回阀第一口和所述止回阀第二口彼此连通地形成单孔形式的止回阀油口。
在至少一个实施方式中，在所述阀槽的周向上，所述背板的至少部分区域的尺寸小于所述阀槽的尺寸，使得所述压力介质能在所述阀槽内轴向流动，且所述阀槽内的所述压力介质能流出所述阀槽。
在至少一个实施方式中，所述止回阀由片状材料冲压和弯折而形成。
在至少一个实施方式中，所述止回阀形成为环形或半环形。
在至少一个实施方式中，所述阀片包括阀头和阀尾，所述阀尾连接所述 阀头和所述主板，
在所述阀槽的周向上，所述阀头的尺寸大于所述阀尾的尺寸。
在至少一个实施方式中，所述止回阀的所述两个阀片的所述阀头相对、所述阀尾相背地设置。
根据本发明的第一方面，提供一种中央阀，其用于凸轮轴相位调节器，并用于控制压力介质在所述凸轮轴相位调节器内的流动，其中，
所述中央阀包括套筒、壳体和根据本发明的止回阀，所述壳体套设在所述套筒外，
所述壳体的周壁上设有至少一组进油孔，每组进油孔包括一个第一进油孔和一个第二进油孔，所述第一进油孔用于与所述第一压力腔连通，所述第二进油孔用于与所述第二压力腔连通，
所述套筒的外周壁部分地向径向内侧凹进而形成至少一个阀槽，所述止回阀设置于所述阀槽内，所述止回阀的两个所述阀片分别位于所述第一进油孔和所述第二进油孔处，以控制所述第一进油孔和所述第二进油孔的开闭。
在至少一个实施方式中，在所述套筒的轴向上，所述阀槽的第一端开放、第二端封闭，所述压力介质能从所述第一端流入所述阀槽。
在至少一个实施方式中，所述阀槽的所述第一端与入口槽相连，
在所述套筒的周向上，所述入口槽的尺寸小于所述阀槽的尺寸。
在至少一个实施方式中，所述阀槽的位于所述中央阀的径向内侧的底部设有套筒进油口，所述压力介质能从所述套筒进油口流出所述阀槽，
所述套筒进油口至少部分不被所述背板遮蔽。
在至少一个实施方式中，在所述阀片处于关闭状态时，所述阀片的朝向所述壳体面与所述壳体的内周壁完全贴合。
在至少一个实施方式中，所述止回阀的数量大于一个，所述阀槽的数量 大于或等于所述止回阀的数量。
根据本发明的止回阀结构简单、制造方便。根据本发明的中央阀具有同样的优点。
附图说明
图1是根据本发明的第一实施方式的中央阀在剖开状态下的进油示意图。
图2是根据本发明的第一实施方式的中央阀的部分结构的分解图。
图3是根据本发明的第一实施方式的止回阀的结构示意图。
图4是根据本发明的第一实施方式的中央阀在剖开状态下的A腔泄油、B腔进油的示意图。
图5是根据本发明的第二实施方式的止回阀的结构示意图。
图6是根据本发明的第三实施方式的止回阀的结构示意图。
图7是根据本发明的第四实施方式的止回阀的结构示意图。
图8是根据本发明的第五实施方式的止回阀的结构示意图。
附图标记说明：
10活塞；11凹腔；
20套筒；21阀槽；20a套筒进油口；22第一腔油槽；22a第一腔出油口；23第二腔油槽；23a第二腔出油口；
30壳体；301第一出油孔；302第二出油孔；311第一进油孔；312第二进油孔；
40止回阀；41阀片；411阀头；412阀尾；42主板；43背板；431止挡部；40a止回阀第一口；40b止回阀第二口；40k止回阀油口；
50弹簧；AX轴向；R径向。
具体实施方式
下面参照附图描述本发明的示例性实施方式。应当理解，这些具体的说明仅用于示教本领域技术人员如何实施本发明，而不用于穷举本发明的所有可行的方式，也不用于限制本发明的范围。
除非特别说明，参照图1和图4，AX表示中央阀的轴向，该轴向AX与活塞10的轴向一致；R表示中央阀的径向，该径向R与活塞10的径向一致。
(第一实施方式)
首先，参照图1至图4介绍根据本发明的第一实施方式的止回阀40及包括止回阀40的中央阀。
参照图1，根据本发明的中央阀包括活塞10、套筒20、壳体30、止回阀40和弹簧50。活塞10、套筒20和壳体30均呈空心的筒形，套筒20套设于活塞10外，壳体30套设于套筒20外。活塞10能相对于套筒20在轴向AX上往复运动，活塞10与套筒20之间设置能在轴向AX上伸缩的弹簧50。
壳体30在轴向AX上是贯通的，其轴向AX上的一端(图中的右端，以下将图1中各部件的右侧的端部称为第一端)为压力介质(例如油)的输入口P，例如可以通过油泵将油泵送至输入口P并使油受控地流入壳体30的内部(即流入中央阀)。
同时参照图2和图4，壳体30在周向上设有至少一组出油孔和至少一组进油孔，每组出油孔包括沿轴向AX排列的第一出油孔301和第二出油孔302，每组进油孔包括沿轴向AX排列的第一进油孔311和第二进油孔312。第一出油孔301和第一进油孔311均与凸轮轴相位调节器的第一压力腔(以下也称A腔)连通，第二出油孔302和第二进油孔312均与凸轮轴相位调节器的第二压力腔(以下也称B腔)连通。
参照图2和图4介绍套筒20。
套筒20在轴向AX上与壳体30固定。套筒20的朝向输入口P的端部(套筒20的第一端)是封闭的。套筒的外周壁向径向内侧凹进地形成至少一个阀槽 21和至少一组油槽。
阀槽21的第一端在轴向AX上开放并与入口槽21a相连，从输入口P流入的油能经过入口槽21a而流至阀槽21。在套筒20的周向上，入口槽21a的尺寸小于阀槽21的尺寸，于是在阀槽21的第一端，入口槽21a在阀槽21的周向两侧部分地凸出，这两个凸出的结构能对下述的安装于阀槽21的止回阀40起到在轴向AX上定位的作用。
阀槽21的第二端(图1中的左端)是封闭的。阀槽21的底部(在径向R上靠内侧的部分)在阀槽21的轴向AX上的大致中间区域开设有在径向R上贯通的套筒进油口20a。阀槽21内的油能通过套筒进油口20a而流至套筒20和活塞10之间。
每组油槽包括沿轴向AX排列的一个第一腔油槽22和一个第二腔油槽23。第一腔油槽22比第二腔油槽23更靠近输入口P，第一腔油槽22的底部(在径向R上靠内侧的部分)在轴向AX上靠近输入口P的区域开设有在径向R上贯通的第一腔出油口22a，第二腔油槽23的底部(在径向R上靠内侧的部分)在轴向AX上远离输入口P的区域开设有在径向R上贯通的第二腔出油口23a。套筒20和活塞10之间的油能经由第一腔出油口22a流至第一腔油槽22，以及经由第二腔出油口23a流至第二腔油槽23。
壳体30上的第一出油孔301至少部分地(优选完全地)与第一腔油槽22连通，第二出油孔302至少部分地(优选完全地)与第二腔油槽23连通；第一进油孔311和第二进油孔312均至少部分地(优选完全地)与阀槽21连通(在不考虑止回阀40的情况下)。
止回阀40安装于阀槽21内，随着A腔和B腔内的油压的变化，止回阀40上的两个阀片会被选择性地打开，使A腔或B腔内的油流入阀槽21内。
接下来，结合图3介绍止回阀40的具体结构。
止回阀40包括主板42、背板43和两个阀片41。主板42大致呈镂空的长条形的片状，两个阀片41均部分地与主板42相连，以使两个阀片41均能相对于 主板42活动。背板43与主板42相连且能在阀片41的打开方向上为阀片41提供支承、避免阀片41的打开角度过大而容易损坏或失效。
在本实施方式中，止回阀40呈大致梯形的环状。梯形环的下底(图3中位于上层的较长的梯形底)形成止回阀40的主板42，梯形环的上底和斜边(图3中的位于下层的部分)均构成背板43。
优选地，止回阀40由片材(例如钢片)冲压、折弯而形成。应当理解，通过折弯而形成大致环形的止回阀40可以在弯折的片材的首尾相接处留有部分缝隙，例如图3中最右侧的缝隙，然而这不是必须的，且本发明对该缝隙的位置不作限制。
阀片41位于主板42的中部，或者说主板42环绕阀片41；更确切地，在本实施方式中，阀片41是通过切割条形板材而形成的，在板材的中部按阀片41的形状切割出槽或缝，该槽或缝的首尾不相连，该槽或缝的轮廓所包围的部分形成阀片41，该槽或缝外围的部分形成主板42。该槽或缝的首尾之间的未切开的部分形成阀片41与主板42的连接部。
在止回阀40安装于套筒20的阀槽21内的情况下，将套筒20的周向(或者说与该周向相切的方向)定义为阀槽21和止回阀40的宽度方向，将套筒20的轴向AX定义为阀槽21和止回阀40的长度方向，将套筒20的径向R定义为阀槽21和止回阀40的深度方向。则有，止回阀40的宽度与阀槽21的宽度W大致相同，止回阀40的长度与阀槽21的长度L大致相同，止回阀40的深度大于或等于阀槽21的深度(止回阀40能以在深度方向上被轻微压缩的方式适应阀槽21的深度)。从而，止回阀40能恰好设置于阀槽21内且通过阀槽21得到定位。
在本实施方式中，阀片41呈长条状，其包括阀头411和阀尾412，阀尾412连接阀头411和主板42。在本实施方式中，两个阀片41的阀头411相对、阀尾412相背。优选地，阀头411的宽度大于阀尾412的宽度。
将阀片41的靠近背板43的一侧(即在止回阀40安装于阀槽21的情况下，阀片41的径向内侧)定义为阀片41的内侧，将阀片41的远离背板43的一侧(即 在止回阀40安装于阀槽21的情况下，阀片41的径向外侧)定义为阀片41的外侧。
在阀片41两侧的油压大致相等的情况下，阀片41不偏离主板42所在的平面，也称这种情况下阀片41处于关闭状态；在阀片41的外侧油压大于内侧油压的情况下，阀头411偏离主板42所在的平面而弯向背板43、直到阀头411接触到背板43，也称这种情况下阀片41处于完全打开状态。
背板43的形状优选为，在阀片41处于打开状态下，背板43能较大面积地接触到阀片41。上述优选形状主要包括两个方面，一是背板43相对于主板42的倾斜角与完全打开状态下的阀片41的倾斜角相适应；二是背板43的尺寸使得背板43能为阀片41提供足够大且均匀的阻挡力。
具体地，在本实施方式中，背板43包括两个相对于主板42倾斜的止挡部431，背板43在止挡部431处为完全打开状态下的阀片41提供支承，止挡部431的倾斜方向和与其相对的阀片41在打开状态下的倾斜方向相仿，越靠近阀片41与主板42的连接部，止挡部431与主板42之间间隔的距离越小。上述设置使得阀片41在频繁的打开和关闭的切换过程中不容易损坏。
背板43上还开设有止回阀第一口40a和止回阀第二口40b。止回阀第一口40a使得油在流经入口槽21a而进入阀槽21的过程中，不会被背板43阻挡，或者说使得油能在阀槽21内轴向流动；止回阀第二口40b使得阀槽21内的油在由套筒进油口20a流至下述凹腔11的过程中，不会被背板43阻挡，或者说使得阀槽21内的压力介质能流出阀槽21。
在本实施方式中，止回阀第二口40b设置在背板43的大致中部，止回阀第一口40a设置在背板43的靠近与主板42的连接部的区域。两个止挡部431中的其中一个止挡部431的主体位于止回阀第一口40a和止回阀第二口40b之间。
在止回阀40安装于阀槽21、且阀片41两侧的油压大致相等的情况下(阀片41处于关闭状态)，两个阀片41均紧贴壳体30的内壁，且两个阀头411分别 完全挡住位于壳体30的第一进油孔311和第二进油孔312，以保证止回阀40的良好的单向阀的作用。为使得上述两个阀头411与两个进油孔的边缘能良好贴合，优选地，至少阀头411与壳体30的位于进油孔周围的内壁的表面弯曲形状相同；例如，壳体30的内壁呈圆柱面，在这种情况下，为方便止回阀40的制作，阀片41和主板42均为曲面状且曲率与上述圆柱面相同；又例如，止回阀40的阀片41和主板42均为平面状，在这种情况下，壳体30的内壁至少在进油孔附近形成平面状(例如通过冲压形成)。
应当理解，由于阀片41的外侧面紧贴壳体30，因此阀片41不能向径向外侧打开，从而第一进油孔311和第二进油孔312只能供油流入阀槽21、而不能供油流出阀槽21。
活塞10的外周的大致中部区域向内凹进地形成环形的凹腔11。凹腔11在轴向AX上的长度满足，在活塞10相对于套筒20轴向移动的过程中，活塞10具有下述位置：(1)凹腔11与套筒进油口20a连通、且凹腔11与第一腔出油口22a连通，(2)凹腔11与套筒进油口20a连通、且凹腔11与第二腔出油口23a连通。
图1中的空心箭头示出了油从输入口P流入凹腔11的路径。为方便示意，图1中只示出了油流入位于上部的凹腔11的路径，而省略油流入位于下部的凹腔11的路径。从输入口P流入的油经过入口槽21a流入阀槽21，之后依次流过止回阀40的止回阀第一口40a和止回阀第二口40b，再流过套筒进油口20a而进入凹腔11。
图4中的空心箭头示出了A腔泄油、B腔进油的路径。此时，活塞10运动至第二腔出油口23a至少部分地与凹腔11相通的位置。油在压力作用下流出A腔，此时第一进油孔311处的阀片41外侧的油压大于内侧的油压，第一进油孔311处的阀片41被打开，油流入阀槽21内并流过止回阀第二口40b而进入凹腔11。凹腔11内的油在压力作用下通过第二腔出油口23a流入第二腔油槽23，第二腔油槽23内的油又在压力作用下通过第二出油孔302流入B腔。
可以理解，当活塞10相对于套筒20运动(即图4中的活塞向右运动)至第一腔出油口22a至少部分地与凹腔11相通的位置，则可以实现A腔进油、B腔泄油。油在压力作用下流出B腔，此时第二进油孔312处的阀片41外侧的油压大于内侧的油压，第二进油孔312处的阀片41被打开，油流入阀槽21内并流过止回阀第二口40b而进入凹腔11。凹腔11内的油在压力作用下通过第一腔出油口22a流入第一腔油槽22，第一腔油槽22内的油又在压力作用下通过第一出油孔301流入A腔。
应当理解，根据本发明的中央阀可以设置至少一个止回阀40，在条件允许的情况下，也可以适当增加止回阀40的数量，以增加油在A腔和B腔之间的流动速度。在本实施方式中，优选地，中央阀包括两个在周向上间隔开的止回阀40。
应当理解，阀槽21同时也是中央阀的进油槽，为保证足够的进油量，例如套筒20上可以设置4个阀槽21，其中2个阀槽21内设有止回阀40，另2个阀槽21内不设止回阀40。设置止回阀40的阀槽21既能供中央阀进油用，又能供A腔或B腔回油用；不设置止回阀40的阀槽21不用于控制A腔或B腔的回油。应当理解，壳体30的周壁的与不设置止回阀40的阀槽21对应的部分不开设进油孔和出油孔(包括第一出油孔301、第二出油孔302、第一进油孔311和第二进油孔312)。
(第二实施方式)
参照图5介绍根据本发明的第二实施方式的止回阀40。第二实施方式是第一实施方式的变型，与第一实施方式相同的部分略去说明。应当理解，图5仅表示出止回阀40的大致结构，图5中未示出与主板42相连的两个阀片及对应于阀片的开口。
本实施方式相比于第一实施方式的主要区别是将第一实施方式中的止回阀第一口40a和止回阀第二口40b合并为一个长条状的止回阀油口40k，即省去原止回阀第一口40a和止回阀第二口40b之间的实体部分，即至少一个止 挡部431由背板43在止回阀油口40k的宽度方向上两侧的部分充当。
(第三实施方式)
参照图6介绍根据本发明的第三实施方式的止回阀40。第三实施方式是第一实施方式的变型，与第一实施方式相同的部分略去说明。应当理解，图6仅表示出止回阀40的大致结构，图6中未示出与主板42相连的两个阀片及对应于阀片的开口。
本实施方式相比于第一实施方式的主要区别是，背板43分成两个间隔开的部分，每个部分形成一个止挡部431，每个止挡部431均与主板42相连。两个止挡部431之间的间隔开的区域形成止回阀第二口40b，其中一个止挡部431上开设有止回阀第一口40a。
(第四实施方式)
参照图7介绍根据本发明的第四实施方式的止回阀40。第四实施方式是第一实施方式的变型，与第一实施方式相同的部分略去说明。应当理解，图7仅表示出止回阀40的大致结构，图7中未示出与主板42相连的两个阀片及对应于阀片的开口。
本实施方式相比于第一实施方式的主要区别是，背板43上不设开口，取而代之的，背板43上至少有部分区域的宽度小于阀槽21的宽度W，以使得入口槽21a(同时参照图2)流入阀槽21的油能轴向地流过阀槽21而流至套筒进油口20a；且套筒20上的套筒进油口20a至少部分不被背板43遮蔽。例如，背板43的中部大部分区域的宽度小于套筒进油口20a在宽度方向上的尺寸。
(第五实施方式)
参照图8介绍根据本发明的第五实施方式的止回阀40。第五实施方式是第三实施方式和第四实施方式的变型，与上述实施方式相同的部分略去说明。应当理解，图8仅表示出止回阀40的大致结构，图8中未示出与主板42相连的两个阀片及对应于阀片的开口。
在本实施方式中，两个止挡部431完全间隔开地设置，每个止挡部431均 与主板42相连。两个止挡部431之间的间隔开的区域形成止回阀第二口40b。
止挡部431上不设开口，油靠流过止挡部431与阀槽21的侧壁之间的空隙而流入阀槽21，因此，至少靠近入口槽21a(同时参照图2)的那个止挡部431至少有部分区域的宽度小于阀槽21的宽度W。
应当理解，上述实施方式、尤其是第二至第五实施方式及其部分方面或特征可以适当地组合。
下面简单说明本发明的上述实施方式的部分有益效果。
(i)本发明使用一体的止回阀40实现了对油在A腔和B腔间流动的控制，止回阀40的结构简单、制造方便，不需要设置多个零部件。
(ii)与止回阀40匹配的套筒20结构简单，通用性强，制造成本低。
(iii)止回阀40的阀槽21可以同时充当油进入中央阀的进油槽，且止回阀40不影响油进入中央阀的量。
应当理解，上述实施方式仅是示例性的，不用于限制本发明。本领域技术人员可以在本发明的教导下对上述实施方式做出各种变型和改变，而不脱离本发明的范围。例如：
(i)在止挡部431能有效支承完全打开状态下的阀头411的情况下，止挡部431也可以不与主板42倾斜地设置。
(ii)止回阀40上的两个阀头411也可以不是相对地设置，例如，两个阀头411也可以同向地或者彼此背对地设置。

Claims (15)

  1. 一种止回阀，其用于设置在凸轮轴相位调节器的中央阀的阀槽(21)内，以控制压力介质从所述凸轮轴相位调节器的第一压力腔内流出、经由所述阀槽(21)而流至第二压力腔，或从所述第二压力腔内流出、经由所述阀槽(21)而流至所述第一压力腔，其中，
    所述止回阀包括主板(42)、背板(43)和两个阀片(41)，
    所述阀片(41)部分地与所述主板(42)相连，使得所述阀片(41)能在所述压力介质的压力作用下改变相对于所述主板(42)的位置，从而具有关闭状态和完全打开状态，
    所述背板(43)在所述阀片(41)处于完全打完状态时为所述阀片(41)提供支承。
  2. 根据权利要求1所述的止回阀，其特征在于，所述背板(43)包括两个止挡部(431)，所述背板(43)在所述止挡部(431)处为处于完全打开状态的所述阀片(41)提供支承，
    所述止挡部(431)相对于所述主板(42)倾斜地设置，越靠近所述阀片(41)与所述主板(42)的连接部，所述止挡部(431)与所述主板(42)之间间隔的距离越小。
  3. 根据权利要求1所述的止回阀，其特征在于，所述背板(43)上设有止回阀第一口(40a)和止回阀第二口(40b)，所述止回阀第一口(40a)使得所述压力介质能在所述阀槽(21)内轴向流动，所述止回阀第二口(40b)使得所述阀槽(21)内的所述压力介质能流出所述阀槽(21)。
  4. 根据权利要求3所述的止回阀，其特征在于，所述止回阀第一口(40a)和所述止回阀第二口(40b)彼此连通地形成单孔形式的止回阀油口(40k)。
  5. 根据权利要求1所述的止回阀，其特征在于，在所述阀槽(21)的周向上，所述背板(43)的至少部分区域的尺寸小于所述阀槽(21)的尺寸， 使得所述压力介质能在所述阀槽(21)内轴向流动，且所述阀槽(21)内的所述压力介质能流出所述阀槽(21)。
  6. 根据权利要求1所述的止回阀，其特征在于，所述止回阀由片状材料冲压和弯折而形成。
  7. 根据权利要求1所述的止回阀，其特征在于，所述止回阀形成为环形或半环形。
  8. 根据权利要求1所述的止回阀，其特征在于，所述阀片(41)包括阀头(411)和阀尾(412)，所述阀尾(412)连接所述阀头(411)和所述主板(42)，
    在所述阀槽(21)的周向上，所述阀头(411)的尺寸大于所述阀尾(412)的尺寸。
  9. 根据权利要求8所述的止回阀，其特征在于，所述止回阀的所述两个阀片(41)的所述阀头(411)相对、所述阀尾(412)相背地设置。
  10. 一种中央阀，其用于凸轮轴相位调节器，并用于控制压力介质在所述凸轮轴相位调节器内的流动，其特征在于，
    所述中央阀包括套筒(20)、壳体(30)和根据权利要求1至9中任一项所述的止回阀(40)，所述壳体(30)套设在所述套筒(20)外，
    所述壳体(30)的周壁上设有至少一组进油孔，每组进油孔包括一个第一进油孔(311)和一个第二进油孔(312)，所述第一进油孔(311)用于与所述第一压力腔连通，所述第二进油孔(312)用于与所述第二压力腔连通，
    所述套筒(20)的外周壁部分地向径向内侧凹进而形成至少一个阀槽(21)，所述止回阀(40)设置于所述阀槽(21)内，所述止回阀(40)的两个所述阀片(41)分别位于所述第一进油孔(311)和所述第二进油孔(312)处，以控制所述第一进油孔(311)和所述第二进油孔(312)的开闭。
  11. 根据权利要求10所述的中央阀，其特征在于，在所述套筒(20)的轴向(AX)上，所述阀槽(21)的第一端开放、第二端封闭，所述压力介质能从所述第一端流入所述阀槽(21)。
  12. 根据权利要求11所述的中央阀，其特征在于，所述阀槽(21)的所述第一端与入口槽(21a)相连，
    在所述套筒(20)的周向上，所述入口槽(21a)的尺寸小于所述阀槽(21)的尺寸。
  13. 根据权利要求10所述的中央阀，其特征在于，所述阀槽(21)的位于所述中央阀的径向内侧的底部设有套筒进油口(20a)，所述压力介质能从所述套筒进油口(20a)流出所述阀槽(21)，
    所述套筒进油口(20a)至少部分不被所述背板(43)遮蔽。
  14. 根据权利要求10所述的中央阀，其特征在于，在所述阀片(41)处于关闭状态时，所述阀片(41)的朝向所述壳体(30)面与所述壳体(30)的内周壁完全贴合。
  15. 根据权利要求10所述的中央阀，其特征在于，所述止回阀(40)的数量大于一个，所述阀槽(21)的数量大于或等于所述止回阀(40)的数量。
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