CN115875100A - Camshaft phase adjuster - Google Patents

Abstract

The invention relates to a camshaft phase adjuster, which is connected to a camshaft to adjust the rotation phase of the camshaft, and comprises a stator, a rotor and a central valve, wherein the rotor is coaxially sleeved in the stator and can rotate relative to the stator, the rotor is provided with an inner cavity and an oil inlet channel communicated with the inner cavity in a fluid mode, pressure fluid from the camshaft flows into the rotor through the oil inlet channel of the rotor, the central valve is installed in the inner cavity of the rotor and can move in the inner cavity along the axial direction of the rotor, and a flow dividing sleeve is arranged between the central valve and the rotor, so that when the central valve moves in the inner cavity in the axial direction, the flow dividing sleeve can divide the pressure fluid flowing into the rotor, and therefore the rotation of the rotor relative to the stator is controlled. According to the camshaft phase adjuster, the number of parts is reduced, the whole structure is simplified, and the assembly is simpler.

Description

Camshaft phase adjuster

Technical Field

The present invention relates to the field of Variable Cam Timing (VCT), and more particularly, to a Camshaft phase adjuster.

Background

It is known that the control times of the gas exchange valves can be influenced by changing the phase between the crankshaft and the camshaft depending on the current operating state of the internal combustion engine, whereby advantageous effects, such as reduction of fuel consumption and production of harmful substances, are achieved. Such a device capable of adjusting the phase between the crankshaft and the camshaft is called a camshaft phase adjuster.

FIG. 1 shows a schematic cross-sectional view of a prior art camshaft phase adjuster. As shown in fig. 1, the camshaft phase adjuster 100' generally includes a stator 10, a rotor 20, and a center valve 80, the rotor 20 is coaxially sleeved in the stator 10 and can rotate relative to the stator 10, the camshaft 1 is mounted on the rotor 20, the center valve 80 is mounted in the rotor 20 and extends into the camshaft 1, and the center valve 80 includes a housing 81, a shunt bush 82, a piston 83, and an elastic member 84, wherein the housing 81 is threaded so that the center valve 80 is fixed to the camshaft 1 by threading, and the piston 83 is mounted in the shunt bush 82 and can move axially relative to the shunt bush 82, whereby the shunting of the pressure fluid flowing from the camshaft 1 into the rotor 20 can be achieved by virtue of the different positions of the piston 83 in the shunt bush 82.

However, as shown in fig. 1, in order to facilitate the tight connection of the central valve 80 to the camshaft 1, the shunt bush 82, the piston 83 and the elastic member 84 are located in the housing 81, which results in a large number of parts of the camshaft phase adjuster 100', and a complicated structural design and assembly process. Furthermore, this results in a high surface accuracy requirement for the individual parts due to the high sealing requirements, which leads to an increased cost of the overall system.

Therefore, a camshaft phase adjuster having a simple structure, easy assembly, and reduced cost is desired.

Disclosure of Invention

The purpose of the present application is to provide a camshaft phase adjuster that has a simple structure, is easy to assemble, and is reduced in cost.

In one aspect, an embodiment of the present application provides a camshaft phase adjuster connected to a camshaft to adjust a rotational phase of the camshaft, the camshaft phase adjuster including a stator, a rotor coaxially sleeved in the stator and rotatable with respect to the stator, wherein the rotor has an inner cavity and an oil inlet passage in fluid communication with the inner cavity, pressure fluid from the camshaft flows into the rotor via the oil inlet passage of the rotor, and a center valve installed in the inner cavity of the rotor and movable in the inner cavity in an axial direction of the rotor, and a flow dividing sleeve is provided between the center valve and the rotor such that the flow dividing sleeve can divide the pressure fluid flowing into the rotor when the center valve moves in the inner cavity in the axial direction, thereby controlling rotation of the rotor with respect to the stator.

According to the foregoing embodiment of the present application, the stator and the rotor jointly form the first hydraulic chamber and the second hydraulic chamber, and the split sleeve includes the first split oil hole capable of being in fluid communication with the first hydraulic chamber and the second split oil hole capable of being in fluid communication with the second hydraulic chamber, the first split oil hole and the second split oil hole being axially spaced apart from each other.

According to the foregoing embodiment of the present application, the rotor has the first oil dividing passage communicating the first hydraulic chamber and the first oil dividing hole, and the second oil dividing passage communicating the second hydraulic chamber and the second oil dividing hole, an inlet of the first oil dividing passage corresponding to the first oil dividing hole, and an inlet of the second oil dividing passage corresponding to the second oil dividing hole.

According to the aforementioned embodiment of the application, the split sleeve still includes the inlet port with oil feed passageway fluid intercommunication, and the inlet port sets up in the position department different with first split oil hole and second split oil hole.

According to the foregoing embodiment of the present application, the oil inlet hole is provided at a position between the first oil dividing hole and the second oil dividing hole in the axial direction, and the oil inlet hole is staggered from the first oil dividing hole and the second oil dividing hole, respectively, in the circumferential direction of the split sleeve.

According to the foregoing embodiment of the present application, the internal cavity has the groove recessed from the inner peripheral side surface of the internal cavity, the groove corresponds to the oil inlet hole of the flow dividing sleeve, and the outlet of the oil inlet passage is exposed to the groove.

According to the foregoing embodiment of the present application, the camshaft phase adjuster further includes a stopper that is installed in the inner cavity of the rotor and abuts against an end of the flow dividing sleeve that is away from the camshaft.

According to the aforementioned embodiment of the present application, the camshaft phase adjuster further includes an adapter that is non-rotatably connected between the rotor and the camshaft and that allows pressure fluid from the camshaft to flow into the oil intake passage, and an end of the flow dividing sleeve that is close to the camshaft abuts against the adapter. The adapter thus connects the rotor and the camshaft in a rotationally fixed manner.

According to the foregoing embodiment of the present application, the center valve includes a piston inserted into the internal cavity from an end of the internal cavity remote from the camshaft and movable in the axial direction in the internal cavity, the flow distribution sleeve is interposed between an outer peripheral side surface of the piston and an inner peripheral side surface of the internal cavity, the piston includes first and second protrusions provided at intervals in the axial direction, the first and second protrusions each extending to the inner peripheral side surface of the flow distribution sleeve.

According to the aforementioned embodiment of the present application, the flow distribution sleeve further includes an oil inlet hole in fluid communication with the oil inlet passage, and the piston further includes a recessed portion provided at the first protrusion and the second protrusion, the recessed portion being in fluid communication with the oil inlet hole.

Thus, according to the camshaft phase adjuster of the embodiment of the present application, the number of parts can be reduced, the entire structure can be simplified, and the assembly can be made simpler by directly disposing the center valve in the inner cavity of the rotor. In addition, can make pressure fluid flow in the internal cavity through set up the oil feed passageway with the internal cavity intercommunication on the rotor, utilize reposition of redundant personnel sleeve and cooperate the reciprocating motion of central valve in reposition of redundant personnel sleeve to realize the effect to pressure fluid reposition of redundant personnel simultaneously, can replace prior art's oil circuit reposition of redundant personnel bush like this to further reduce spare part figure, and simplify overall structure, thereby reduce camshaft phase place adjuster's processing manufacturing cost. In addition, because the split sleeve is arranged between the rotor and the central valve, the inner cavity of the rotor does not need to be subjected to finish machining, and therefore the manufacturing requirement on the rotor is reduced, and the machining and manufacturing cost of the camshaft phase adjuster is reduced.

Drawings

Features, advantages and technical effects of exemplary embodiments of the present application will be described below by referring to the accompanying drawings.

FIG. 1 shows a schematic cross-sectional view of a prior art camshaft phase adjuster.

FIG. 2 shows a schematic cross-sectional view of a camshaft phase adjuster according to an embodiment of the present application.

FIG. 3 shows another cross-sectional schematic view of a camshaft phase adjuster according to an embodiment of the present application.

Fig. 4A and 4B show a perspective view and a cross-sectional view, respectively, of a rotor of a camshaft phase adjuster according to an embodiment of the present application.

FIG. 5 shows a schematic cross-sectional view of a camshaft phase adjuster according to an embodiment of the present application with the center valve removed.

FIG. 6 shows a schematic perspective view of a split sleeve of a camshaft phase adjuster according to an embodiment of the present application.

In the drawings, the drawings are not necessarily drawn to scale.

Detailed Description

Embodiments of the present application will be described in further detail below with reference to the drawings and examples. The following detailed description of the embodiments and the accompanying drawings are provided to illustrate the principles of the application, but are not intended to limit the scope of the application, i.e., the application is not limited to the described embodiments.

In the description of the present application, it is to be noted that, unless otherwise specified, "a plurality" means two or more; the terms "inner", "outer", and the like, indicate an orientation or positional relationship merely for convenience in describing the present application and for simplicity in description, and do not indicate or imply that the referenced devices or elements must have a particular orientation, be constructed and operated in a particular orientation, and therefore should not be construed as limiting the present application. Furthermore, the terms "first," "second," and the like are used for descriptive purposes only and are not to be construed as indicating or implying relative importance. "vertical" is not strictly vertical, but is within the tolerance of the error. "parallel" is not strictly parallel but within the tolerance of the error.

The following description is given with the directional terms as they are used in the drawings and not intended to limit the specific structure of the present application. In the description of the present application, it is also to be noted that, unless otherwise explicitly specified or limited, the terms "mounted," "connected," and "connected" are to be construed broadly, e.g., as meaning either a fixed connection, a removable connection, or an integral connection; may be directly connected or indirectly connected through an intermediate. The specific meaning of the above terms in this application can be understood as appropriate by one of ordinary skill in the art.

For a better understanding of the present application, embodiments of the present application are described below with reference to fig. 2 to 5.

As shown in fig. 2 to 5, a camshaft phase adjuster 100 is connected to the camshaft 1 to adjust the rotational phase of the camshaft 1, thereby controlling the advance/retard opening and closing of valves connected to the camshaft 1. Illustratively, the camshaft phase adjuster 100 is connected to one side of the camshaft 1, for example, by bolts or directly welded to one side of the camshaft 1. The camshaft phase adjuster 100 includes a stator 10, a rotor 20, a center valve 30, a flow dividing sleeve 40, a stopper 50, and an adapter 60.

The rotor 20 is coaxially fitted within the stator 10 and is capable of rotating relative to the stator 10 under the drive of the central valve 30. The rotor 20 has a body 21 and a plurality of blades 22 fixedly provided to the body 21. The rotor 20 may form a first hydraulic chamber and a second hydraulic chamber together with its vanes 22 and the stator 10. The first and second hydraulic chambers are alternately distributed along the outer circumference of the rotor 20, and no fluid communication is formed therebetween. Accordingly, the rotation of the rotor 20 with respect to the stator 10 may be controlled by selectively injecting the pressure fluid into the first and second hydraulic chambers. The rotor 20 is typically made of a less wear resistant piece of metallurgy.

As shown in fig. 4A and 4B, the rotor 20 has an internal cavity 23 and an oil inlet passage P in fluid communication with the internal cavity 23. The inner cavity 23 is provided substantially at the radial center of the rotor 20 and extends in the axial direction of the rotor 20. The internal cavity 23 is substantially cylindrical. The oil intake passage P extends substantially in the axial direction of the rotor 20. The oil inlet passage P may have a sectional shape such as a circle, an ellipse, a semicircle, a rectangle, or the like. For example, fig. 4A illustrates that the oil feed passage P has a rectangular cross-sectional shape. An inlet of the oil feed passage P is provided at a side of the rotor 20 connected with the camshaft 1 and is capable of allowing the pressure fluid from the camshaft 1 to enter, and an outlet of the oil feed passage P is exposed at the inner cavity 23 of the rotor 20. Therefore, the pressure fluid from the camshaft 1 can flow into the inner cavity 23 of the rotor 20 via the oil intake passage P of the rotor 20. The number of the oil inlet passages P may be plural, and the plural oil inlet passages P are arranged at intervals in the circumferential direction of the rotor 20. Preferably, the plurality of oil feed passages P are evenly spaced along the circumference of the rotor 20. For example, fig. 4A illustrates that four oil inlet passages P are evenly spaced in the circumferential direction of the rotor 20.

As shown in fig. 4B, a first oil distribution passage a and a second oil distribution passage B are also formed in the rotor 20. The first oil distribution passage a extends substantially radially along the body 23 of the rotor 20, and an inlet of the first oil distribution passage a is exposed to the internal cavity 23 of the rotor 20 and an outlet of the first oil distribution passage a is exposed to the first hydraulic chamber. Therefore, the first oil distribution passage a is in fluid communication with the first hydraulic chamber but not with the second hydraulic chamber. The second oil distribution passage B extends substantially radially along the body 23 of the rotor 20, and an inlet of the second oil distribution passage B is exposed to the inner cavity 23 of the rotor 20, and an outlet of the second oil distribution passage B is exposed to the second hydraulic chamber. Therefore, the second branch oil passage B is in fluid communication with the second hydraulic chamber but not with the first hydraulic chamber.

As shown in fig. 4B, the inlet of the first branch oil passage a and the inlet of the second branch oil passage B are provided at different positions from the outlet of the oil-taking passage P in the axial direction of the rotor 20. Also, the inlet of the first oil distribution passage a and the inlet of the second oil distribution passage B are provided at different positions from the outlet of the oil intake passage P in the circumferential direction of the rotor 20. In other words, the oil-taking passage P does not extend to any position of both the first oil distribution passage a and the second oil distribution passage B.

Further, as shown in fig. 4B, the internal cavity 23 includes a groove 24 recessed from the inner peripheral side surface of the internal cavity 23, and the outlet of the oil-taking passage P is exposed to the groove 24, thereby being exposed to the internal cavity 23. The groove 24 may be annular. Of course, in other embodiments, the number of the grooves 24 may be multiple, and multiple grooves 24 may be distributed at intervals along the circumference of the rotor 20 as long as they can expose the outlet of the oil feeding passage P to the internal cavity 23. The groove 24 can accommodate a part of the pressure fluid flowing from the oil feed passage P, whereby the fluid dynamic performance of the pressure fluid can be improved during the movement of the center valve 30. As shown in fig. 4B, the oil feed passage P forms an L-shaped oil passage with the groove 24, whereby the pressure fluid entering the oil feed passage P enters the internal cavity 23 via the inner peripheral side face of the internal cavity 23.

Also, the groove 24 is provided at a position different from the inlet of the first oil distribution passage a and the inlet of the second oil distribution passage B in the axial direction of the rotor 20. Exemplarily, the groove 24 is provided at a position between an inlet of the first oil distribution passage a and an inlet of the second oil distribution passage B in the axial direction of the rotor 20. Therefore, the outlet of the oil-taking passage P is provided at a position between the inlet of the first oil distribution passage a and the inlet of the second oil distribution passage B in the axial direction of the rotor 20.

Referring again to fig. 2 and 3, the central valve 30 and the flow divider sleeve 40 are both mounted in the interior cavity 23 of the rotor 20. The central valve 30 includes a piston 31 and an elastic member 32. The piston 31 is inserted into the internal cavity 23 from an end of the internal cavity 23 away from the camshaft 1 and is movable in the axial direction of the rotor 20 in the internal cavity 23 by, for example, an electromagnet (not shown) mounted at an end (i.e., the left end in fig. 2) of the piston 31 away from the elastic member 32. The elastic member 32 is connected to the piston 31 to apply an elastic force to the piston 31 in an axial direction so as to restore the piston 31. In one example, the resilient member 32 is a spring. The elastic member 32 is provided at an end (i.e., the left end in fig. 2) of the piston 31 near the camshaft 23. Accordingly, the piston 31 is located between the electromagnet (not shown) and the elastic member 32, whereby the piston 31 can reciprocate in the axial direction of the rotor 20 within the internal cavity 23 by the driving of both the electromagnet (not shown) and the elastic member 32.

A flow sleeve 40 is disposed between the central valve 30 and the rotor 20. Specifically, the flow dividing sleeve 40 is interposed between the outer peripheral side surface of the piston 31 and the inner peripheral side surface of the internal cavity 23 of the rotor 20. Thus, when the piston 31 moves axially in the flow dividing sleeve 40, the flow dividing sleeve 40 can divide the pressure fluid flowing into the internal cavity 23 to selectively introduce the pressure fluid into the first or second hydraulic chamber by the position of the piston 31 in the flow dividing sleeve 40, thereby controlling the rotation of the rotor 20 relative to the stator 10.

Therefore, according to the camshaft phase adjuster 100 of the embodiment of the present invention, the oil inlet passage P communicating with the internal cavity 23 is provided on the rotor 20 to allow the pressure fluid to flow into the internal cavity 23, and the pressure fluid is divided by the flow dividing sleeve 40 in cooperation with the reciprocal movement of the center valve 30 in the internal cavity 23, so that the prior art oil path flow dividing bush can be replaced to further reduce the number of parts and simplify the overall structure, thereby reducing the manufacturing cost of the camshaft phase adjuster.

With continued reference to fig. 2 and 3, the piston 31 is generally hollow cylindrical in shape. The piston 31 is formed with a first protrusion 311 and a second protrusion 312 that are provided at intervals in the axial direction of the rotor 20. The first projection 311 and the second projection 312 extend radially outward from the outer peripheral surface of the piston 31 to the inner peripheral side surface of the flow dividing sleeve 40, respectively. When the camshaft phase adjuster 100 is operated, the electromagnet can push the piston 31 in the axial direction according to a control signal from an engine control system, so that the first protrusion 311 and the second protrusion 312 selectively open and close the first oil distribution passage a to the first hydraulic chamber and the second oil distribution passage B to the second hydraulic chamber to control the flow of the pressure fluid into the first hydraulic chamber and the second hydraulic chamber, thereby adjusting the rotation angle of the rotor 20 relative to the stator 10 to advance or retard the opening of the valve.

The piston 31 further includes a groove 313 formed between the first protrusion 311 and the second protrusion 312, the groove 313 being in fluid communication with the groove 24 of the internal cavity 23. Therefore, the groove 313 can also accommodate a part of the pressure fluid flowing from the oil feed passage P, thereby improving the fluid dynamic performance of the pressure fluid during the movement of the piston 31.

In addition, as shown in fig. 2 and 3, a circular arc transition portion is formed between the first protrusion 311 and the groove 313 and/or between the second protrusion 312 and the groove 313, so that the stress concentration problem caused by machining is reduced, and the service life of the piston 31 is prolonged. The piston 31 further includes an axially extending central bore and a through bore extending radially through the piston 31 and communicating with the central bore, the through bore being adapted to communicate pressurized fluid within the internal cavity 23 with the external environment.

The flow sleeve 40 is typically made of a steel member having a high wear resistance. Therefore, although the rotor 20 is made of a metallurgical member having poor wear resistance, since the flow dividing sleeve 40 having high wear resistance is provided between the rotor 20 and the center valve 30, it is not necessary to finish-machine the inner cavity 23 of the rotor 20, the first oil dividing passage a, and the second oil dividing passage B, and thus the manufacturing requirement for the rotor 20 is reduced, thereby reducing the manufacturing cost of the camshaft phase adjuster 100.

As shown in fig. 2 and 3, the flow divider sleeve 40 generally forms an interference fit with the inner peripheral side surface of the internal cavity 23 of the rotor 20. As shown in fig. 2, the stop 50 is mounted in the inner cavity 23 of the rotor 20 and abuts against the end of the flow dividing sleeve 40 remote from the camshaft 1. The adapter 60 is connected in a rotationally fixed manner (for example by means of screws) between the rotor 20 and the camshaft 1 and bears against one end of the shunt sleeve 40 close to the camshaft 1. Stop 50 and adapter 60 cooperate to limit axial movement of shunt sleeve 40. Further, the adapter 60 has a passage (not shown) that allows the pressure fluid from the camshaft 1 to flow into the oil intake passage P of the rotor 20. In addition, a check valve and a filter can be arranged between the rotor 20 and the camshaft 1, the check valve only allows pressure fluid to flow from the camshaft 1 to the rotor 20, but does not allow the pressure fluid to flow from the rotor 20 to the camshaft, and the filter screen can reduce impurities in the pressure fluid entering the oil inlet channel P, so that reliable operation of the camshaft phase adjuster is ensured.

As shown in fig. 5, the flow dividing sleeve 40 includes an oil inlet hole 41, a first oil dividing hole 42, and a second oil dividing hole 43. The oil inlet hole 41, the first oil dividing hole 42, and the second oil dividing hole 43 each penetrate the side wall of the dividing sleeve 40. The oil inlet hole 41, the first oil dividing hole 42 and the second oil dividing hole 43 are disposed at different positions and spaced apart from each other. Specifically, the oil inlet hole 41 is provided at a substantially central position of the split sleeve 40, and the first and second oil split holes 42 and 43 are respectively provided at both sides of the oil inlet hole 41, and the oil inlet hole 41 is disposed offset from the first and second oil split holes 42 and 43 by a distance in the circumferential direction of the split sleeve 40.

As shown in fig. 5, the oil inlet hole 41 is in fluid communication with the groove 24 of the internal cavity 23 and thus with the oil inlet passage P of the rotor 20. The first oil-dividing hole 42 corresponds to the first oil-dividing passage a, and thus is in fluid communication with the first hydraulic chamber via the first oil-dividing passage a. The second branch oil hole 43 corresponds to the second branch oil passage B, and thus is in fluid communication with the second hydraulic chamber via the second branch oil passage B. Preferably, the number of the oil inlet holes 41 may be plural, and a plurality of the oil inlet holes 41 are arranged at regular intervals along the circumferential direction of the flow dividing sleeve 40, and the plurality of the oil inlet holes 41 correspond to the plurality of the oil inlet passages P of the rotor 20. Similarly, the number of the first oil dividing holes 42 may be plural, and a plurality of the first oil dividing holes 42 are uniformly spaced along the circumferential direction of the dividing sleeve 40, the plurality of first oil dividing holes 42 corresponding to the plurality of first oil dividing passages a of the rotor 20. Likewise, the number of the second oil dividing holes 43 may be plural, and plural second oil dividing holes 43 are arranged at regular intervals in the circumferential direction of the dividing sleeve 40, the plural second oil dividing holes 43 corresponding to the plural second oil dividing passages B of the rotor 20.

Thus, according to an embodiment of the present invention, the camshaft phase adjuster 100 may have two modes, i.e., a first split mode and a second split mode. In the first split mode, the oil inlet passage P is in fluid communication with the first hydraulic chamber, but not with the second hydraulic chamber, via the oil inlet hole 41, the first oil-dividing hole 42, and the first oil-dividing passage a in this order. In the second split mode, the oil inlet passage P is in fluid communication with the second hydraulic chamber, but not with the first hydraulic chamber, via the oil inlet hole 41, the second oil split hole 43, and the second oil split passage B in this order. Accordingly, when the center valve 30 is axially moved in the flow dividing sleeve 40, the camshaft phase adjuster 100 can be switched between the first flow dividing mode and the second flow dividing mode by means of different positions of the piston 31, thereby selectively directing the pressure fluid entering the rotor 20 into the first hydraulic chamber and the second hydraulic chamber, thereby controlling the rotation of the rotor 20 relative to the stator 10.

Preferably, the camshaft phase adjuster 100 may also have a third mode, i.e., a holding mode in which the first hydraulic chamber is in fluid communication with neither the oil inlet passage P nor the outside environment via the oil inlet hole 41, the first oil dividing hole 42, and the first oil dividing passage a, while the second hydraulic chamber is in fluid communication with neither the oil inlet passage P nor the outside environment via the oil inlet hole 41, the second oil dividing hole 43, and the second oil dividing passage B. Therefore, the capacity of the pressure fluid in each of the first hydraulic chamber and the second hydraulic chamber remains unchanged, whereby the position of the rotor 20 relative to the stator 10 can be maintained unchanged.

Thus, the camshaft phase adjuster 100 can be switchably operated between the first split mode, the second split mode, and the holding mode by means of axial movement of the center valve 30. The operation thereof will be described in detail with reference to fig. 2 and 3.

Fig. 2 and 3 show schematic views of the camshaft phase adjuster 100 in the first split mode. When the camshaft phase adjuster 100 is in the first split mode, the piston 31 moves leftward to a first position while the elastic member 32 is in a first compressed state. At this time, the first protrusion 311 is located at the left side of the first oil dividing hole 42 of the flow dividing sleeve 40 (corresponding to the inlet of the first oil dividing passage a of the rotor 20), and the oil inlet passage P is brought into fluid communication (not shown) with the first oil dividing passage a via the first oil dividing hole 42 to allow the pressure fluid, which has entered the rotor 20 via the oil inlet passage P, to enter the first hydraulic chamber via the oil inlet hole 41, the first oil dividing hole 42, and the first oil dividing passage a in this order, while the second protrusion 312 is located at a position between the oil inlet hole 41 and the second oil dividing hole 43 of the flow dividing sleeve 40 in the axial direction, thereby restricting the pressure fluid from flowing into the second hydraulic chamber via the second oil dividing hole 43 and the second oil dividing passage B. Preferably, the second protrusion 312 may partially block the second oil distribution hole 43 and the second oil distribution passage B. The pressure fluid introduced into the first hydraulic chamber forces the rotor 20 to rotate in a direction (clockwise) to press the second hydraulic chamber, and with such rotation, the pressure fluid in the second hydraulic chamber flows into the center hole of the piston 34 along the second oil distribution passage B and the second oil distribution hole 43, and then flows out of the piston 34 through the through hole. The flow direction of the pressure fluid in the first split flow mode is shown by the arrows in fig. 2.

Fig. 2 and 3 show only one extreme position of the piston 31, but of course the piston 31 according to the embodiment of the present application may have other positions than this extreme position according to actual requirements, so as to more precisely adjust the rotation angle of the rotor 20 relative to the stator 10 to decide the early or late opening of the valve according to the operating condition of the engine.

For example, the camshaft phase adjuster 100 according to the embodiment of the present invention may be selectively placed in the second split mode in which the piston 31 moves rightward to a second position (not shown in the drawings) and the elastic member 32 is placed in a second compressed state in which the amount of compression of the elastic member 32 in the second compressed state is greater than the amount of compression of the elastic member 32 in the first compressed state. At this time, the second protrusion 312 is located at the right side of the second oil dividing hole 43 of the flow dividing sleeve 40 (corresponding to the inlet of the second oil dividing passage B of the rotor 20) to fluidly communicate the oil inlet passage P with the second oil dividing passage B to allow the pressure fluid, which has entered the rotor 20 via the oil inlet passage P, to enter the second hydraulic chamber via the oil inlet hole 41, the second oil dividing hole 43, and the second oil dividing passage B in this order, while the first protrusion 311 is located at a position axially between the oil inlet hole 41 and the first oil dividing hole 42 of the flow dividing sleeve 40, thereby restricting the pressure fluid from flowing into the first hydraulic chamber via the first oil dividing hole 42 and the first oil dividing passage a. Preferably, the first protrusion 311 may partially block the first oil dividing hole 42 and the first oil dividing passage a. The pressure fluid entering the second hydraulic chamber forces the rotor 20 to rotate in a direction (e.g., counterclockwise) that presses the first hydraulic chamber, and with such rotation, the pressure fluid in the first hydraulic chamber flows into the center hole of the piston 34 along the first branch oil passage a and the first branch oil hole 42, and further flows out of the piston 34 through the through hole.

For another example, the camshaft phase adjuster 100 according to the embodiment of the present invention may also be in the holding mode, in which the first protrusion 311 is located at the first oil dividing hole 42 of the flow dividing sleeve 40 in the axial direction, thereby blocking the first oil dividing hole 42 and the first oil dividing passage a, so as to prohibit the pressure fluid from flowing into the first hydraulic chamber via the first oil dividing hole 42 and the first oil dividing passage a, and prohibit the pressure fluid in the first hydraulic chamber from flowing out via the first oil dividing passage a and the first oil dividing hole 42, so as to keep the volume of the pressure fluid in the first hydraulic chamber constant; the second protrusion 312 is located at the second oil dividing hole 43 of the flow dividing sleeve 40 in the axial direction, thereby blocking the second oil dividing hole 43 and the second oil dividing passage B, so as to prohibit the pressure fluid from flowing into the second hydraulic chamber via the second oil dividing hole 43 and the second oil dividing passage B, and at the same time prohibit the pressure fluid in the second hydraulic chamber from flowing out via the second oil dividing passage B and the second oil dividing hole 43, so as to keep the volume of the pressure fluid in the second hydraulic chamber constant. That is, in the holding mode, the oil-intake passage P is not in fluid communication with either the first oil distribution passage a or the second oil distribution passage B, while the first hydraulic chamber is not in communication with the outside environment via the first oil distribution passage a and the first oil distribution hole 42, and the second hydraulic chamber is not in communication with the outside environment via the second oil distribution passage B and the second oil distribution hole 43, respectively, which can ensure that the respective pressure fluid capacities of the first hydraulic chamber and the second hydraulic chamber remain unchanged, so that the position of the rotor 20 relative to the stator 10 can be maintained unchanged.

While the present application has been described with reference to preferred embodiments, various modifications may be made and equivalents may be substituted for elements thereof without departing from the scope of the present application, and in particular, features shown in the various embodiments may be combined in any manner as long as there is no structural conflict. The present application is not intended to be limited to the particular embodiments disclosed herein, but rather to cover all embodiments falling within the scope of the appended claims.

Claims (10)

1. A camshaft phase adjuster (100) connected to a camshaft to adjust a rotational phase of the camshaft, the camshaft phase adjuster (100) including a stator (10), a rotor (20), and a center valve (30), the rotor (20) being coaxially fitted within the stator (10) and being rotatable relative to the stator (10), wherein,

the rotor (20) having an inner cavity (23) and an oil inlet passage (P) in fluid communication with the inner cavity (23), pressure fluid from the camshaft flowing into the rotor (20) via the oil inlet passage (P) of the rotor (20), the central valve (30) being mounted in the inner cavity (23) of the rotor (20) and being movable in the inner cavity (23) in the axial direction of the rotor (20),

a flow dividing sleeve (40) is provided between the central valve (30) and the rotor (20) such that when the central valve (30) is moved axially in the internal cavity (23), the flow dividing sleeve (40) can divide the pressure fluid flowing into the rotor (20) to control the rotation of the rotor (20) relative to the stator (10).

2. The camshaft phase adjuster (100) of claim 1, wherein

The stator (10) and the rotor (20) together form a first hydraulic chamber and a second hydraulic chamber, the flow dividing sleeve (40) includes a first oil dividing hole (42) capable of being in fluid communication with the first hydraulic chamber and a second oil dividing hole (43) capable of being in fluid communication with the second hydraulic chamber, and the first oil dividing hole (42) and the second oil dividing hole (43) are disposed spaced apart from each other in the axial direction.

3. The camshaft phase adjuster (100) of claim 2, wherein

The rotor (20) has a first oil distribution passage (A) communicating the first hydraulic chamber and the first oil distribution hole (42), an inlet of the first oil distribution passage (A) corresponding to the first oil distribution hole (42), and a second oil distribution passage (B) communicating the second hydraulic chamber and the second oil distribution hole (43), an inlet of the second oil distribution passage (B) corresponding to the second oil distribution hole (43).

4. The camshaft phase adjuster (100) of claim 2, wherein

The flow dividing sleeve (40) further includes an oil inlet hole (41) in fluid communication with the oil inlet passage (P), the oil inlet hole (41) being provided at a position different from the first oil dividing hole (42) and the second oil dividing hole (43).

5. The camshaft phase adjuster (100) of claim 4, wherein

The oil inlet hole (41) is provided at a position between the first oil dividing hole (42) and the second oil dividing hole (43) in the axial direction, and the oil inlet hole (41) is mutually staggered from the first oil dividing hole (42) and the second oil dividing hole (43) in the circumferential direction of the branch sleeve (40), respectively.

6. The camshaft phase adjuster (100) of claim 4, wherein

The inner cavity (23) has a groove (24) recessed from an inner peripheral side surface of the inner cavity (23), the groove (24) corresponds to the oil inlet hole (41) of the flow dividing sleeve (40), and an outlet of the oil inlet passage (P) is exposed to the groove (24).

7. The camshaft phase adjuster (100) of claim 1, wherein

The camshaft phase adjuster (100) further comprises a stop (50), the stop (50) being mounted within the internal cavity (23) of the rotor (20) and abutting against an end of the flow dividing sleeve (40) remote from the camshaft.

8. The camshaft phase adjuster (100) of claim 1, wherein

The camshaft phase adjuster (100) further comprises an adapter (60), the adapter (60) being connected in a rotationally fixed manner between the rotor (20) and the camshaft and allowing a pressure fluid from the camshaft to flow into the oil feed channel (P), and an end of the flow dividing sleeve (40) close to the camshaft abuts against the adapter (60).

9. The camshaft phase adjuster (100) of claim 1, wherein

The center valve (30) includes a piston (31) that is inserted into the internal cavity (23) from an end of the internal cavity (23) remote from the camshaft and is movable in the axial direction in the internal cavity (23), the flow distribution sleeve (40) is interposed between an outer peripheral side surface of the piston (31) and an inner peripheral side surface of the internal cavity (23), the piston (31) includes first protrusions (311) and second protrusions (312) that are provided at intervals in the axial direction, and the first protrusions (311) and the second protrusions (312) each extend to the inner peripheral side surface of the flow distribution sleeve (40).

10. The camshaft phase adjuster (100) of claim 9, wherein

The flow distribution sleeve (40) further comprises an oil inlet hole (41) in fluid communication with the oil inlet passage (P), and the piston (31) further comprises a recess (313) provided between the first protrusion (311) and the second protrusion (312), the recess being in fluid communication with the oil inlet hole (41).

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