WO2023019599A1

WO2023019599A1 - Camshaft phase regulator

Info

Publication number: WO2023019599A1
Application number: PCT/CN2021/113914
Authority: WO
Inventors: 何艳桦
Original assignee: 舍弗勒技术股份两合公司
Priority date: 2021-08-20
Filing date: 2021-08-20
Publication date: 2023-02-23

Abstract

A camshaft phase regulator (100), which is connected to a camshaft (1) to regulate a rotational phase of the camshaft (1). The camshaft phase regulator (100) comprises a stator (10), a rotor (20) and a central valve (30), wherein the rotor (20) is coaxially sleeved inside the stator (10) and can rotate relative to the stator (10); the rotor (20) is provided with an inner cavity (23), and an oil intake channel (P) in fluid communication with the inner cavity (23); a pressure fluid from the camshaft (1) flows into the rotor (20) through the oil intake channel (P) of the rotor (20); and the central valve (30) is mounted in the inner cavity (23) of the rotor (20) and can move in the inner cavity (23) in an axial direction of the rotor (20), so as to divert the pressure fluid flowing into the rotor (20), thereby controlling the rotation of the rotor (20) relative to the stator (10).

Description

camshaft phase adjuster

technical field

This application relates to the technical field of Variable Camshaft Timing (VCT for short), in particular to a camshaft phase adjuster.

Background technique

It is known that, according to the current operating conditions of the internal combustion engine, the timing of the gas exchange valves can be influenced by changing the phase between the crankshaft and the camshaft, thereby achieving beneficial effects such as reduced fuel consumption and the generation of harmful substances . This device that can adjust the phase between the crankshaft and the camshaft is called a camshaft phase adjuster.

1 shows a prior art camshaft phaser 100' comprising a stator 10; a rotor 20 rotatably disposed within the stator 10 and comprising a central bore axially penetrating the rotor 20; and a central valve 40, It is installed in the central hole of the rotor 20, and includes a threaded housing 41, an oil passage diversion bushing 42 located in the housing 41, and an oil passage diversion bushing 42 installed in the oil passage diversion bushing 42 and capable of opposing the oil passage diversion bushing. 42 reciprocating piston 43 . The rotor 20 and the stator 10 jointly form a first hydraulic chamber and a second hydraulic chamber (not shown in FIG. 1 ), and the inside of the rotor 20 is formed with a first oil distribution channel and a The second oil distribution channel. A first through hole 411 and a second through hole 412 respectively corresponding to the first oil distribution passage and the second oil distribution passage are formed on the housing 41 . There is a clearance fit between the outer surface of the housing 41 and the inner surface of the central hole of the rotor 20 . The central valve 40 is connected to the camshaft (not shown in FIG. 1 ) by threads on the housing 1 . Thus, with the help of the reciprocating movement of the piston 43, the pressure fluid from the camshaft can selectively enter the first hydraulic chamber through the first through hole 411 and the first oil distribution passage, so as to push the Zhuangzi 20 to rotate clockwise relative to the stator 10 And the valve is opened in advance or delayed, and enters the second hydraulic chamber through the second through hole 412 and the second oil distribution passage, so as to push the Zhuangzi 20 to rotate counterclockwise relative to the stator 10 to advance or delay the opening of the valve.

However, in the camshaft phase adjuster 100', the number of parts is large, the structural design and assembly process are relatively complicated, and the requirements for the surface accuracy of each part are relatively high due to the need for sealing.

Therefore, there is an urgent need for a camshaft phase adjuster with simple structure, easy assembly and reduced cost.

Contents of the invention

The purpose of the present application is to provide a camshaft phase adjuster with simple structure, easy assembly and reduced cost.

On the one hand, the embodiment of the present application proposes a camshaft phase adjuster, which is connected to the camshaft to adjust the rotation phase of the camshaft, the camshaft phase adjuster includes a stator, a rotor and a central valve, and the rotor is coaxially sleeved In the stator and can rotate relative to the stator, wherein the rotor has an internal cavity and an oil inlet passage fluidly connected with the internal cavity, the pressure fluid from the camshaft flows into the rotor through the oil inlet passage of the rotor, and the central valve is installed on The internal cavity of the rotor can move in the internal cavity along the axial direction of the rotor to divide the pressure fluid flowing into the rotor, so as to control the rotation of the rotor relative to the stator.

According to the foregoing embodiments of the present application, there are multiple oil inlet passages, the plurality of oil inlet passages are arranged at intervals along the circumference of the rotor, and each oil inlet passage extends axially.

According to the foregoing embodiments of the present application, the stator and the rotor jointly form the first hydraulic chamber and the second hydraulic chamber, and when the central valve moves axially in the inner cavity, the oil inlet channel can be selectively connected with the first hydraulic chamber In fluid communication with the second hydraulic chamber.

According to the foregoing embodiments of the present application, the rotor has a first oil distribution channel in fluid communication with the first hydraulic chamber and a second oil distribution channel in fluid communication with the second hydraulic chamber, and when the central valve is in the inner cavity in the axial direction When moving, the camshaft phase adjuster can communicate with the first hydraulic chamber via the first oil distribution passage and not communicate with the second hydraulic chamber in the first split mode and the oil inlet passage via the second oil distribution passage and the second hydraulic chamber. The hydraulic chamber is switched between a second split mode in which the hydraulic chamber is not in fluid communication with the first hydraulic chamber.

According to the foregoing embodiments of the present application, the camshaft phase adjuster also has an oil inlet passage that is neither in fluid communication with the first hydraulic chamber nor with the second hydraulic chamber when the central valve moves axially in the inner cavity hold mode.

According to the foregoing embodiments of the present application, the outlet of the oil inlet passage is disposed at a different position from the inlets of the first oil separation passage and the inlets of the second oil separation passage.

According to the foregoing embodiments of the present application, the inner cavity has a groove recessed from the inner peripheral side of the inner cavity, the outlet of the oil inlet passage is exposed to the groove, and the groove is axially arranged on the same side as the first oil distribution passage. The entrance of the inlet and the inlet of the second oil distribution channel are at different positions. Preferably, the groove is arranged axially at a position between the inlet of the first oil-separating passage and the inlet of the second oil-separating passage.

According to the foregoing embodiments of the present application, the central valve includes a piston inserted into the inner cavity from one end of the inner cavity away from the camshaft and capable of axially moving in the inner cavity, and the piston includes a first axially spaced piston. a protrusion and a second protrusion, and when the camshaft phase adjuster is in the first split mode, the second protrusion restricts the flow of pressure fluid into the second hydraulic chamber via the second oil split passage, and when the camshaft phase adjuster is in the In the second flow splitting mode, the first protrusion restricts pressure fluid from flowing into the first hydraulic chamber through the first oil splitting passage.

According to the foregoing embodiments of the present application, the inner cavity has a groove recessed from the inner peripheral side of the inner cavity, the outlet of the oil inlet passage is exposed to the groove, and the piston further includes a groove disposed on the first protrusion and the second protrusion. The recess, the recess corresponds to the groove.

According to the foregoing embodiments of the present application, the central valve further includes an elastic member disposed in the inner cavity and connected to the piston to apply elastic force to the piston in an axial direction.

According to the camshaft phase adjuster of the embodiment of the present application, the number of components can be reduced, the overall structure can be simplified, and the assembly can be simplified by disposing the central valve in the internal cavity of the rotor. In addition, the pressure fluid can flow into the internal cavity by providing an oil inlet channel communicating with the internal cavity on the rotor, and cooperate with the reciprocating movement of the central valve in the internal cavity to achieve the effect of splitting the pressure fluid. It can replace the oil passage diverting bushing in the prior art to further reduce the number of parts and simplify the overall structure, thereby reducing the processing and manufacturing cost of the camshaft phase adjuster.

Description of drawings

The features, advantages, and technical effects of the 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 camshaft phase adjuster in the prior art.

Fig. 2 shows a schematic perspective view of the overall structure of a camshaft phase adjuster according to an embodiment of the present application.

Fig. 3 shows a schematic perspective view of a partial structure of a camshaft phase adjuster according to an embodiment of the present application.

FIG. 4 shows a schematic cross-sectional view of a rotor of a camshaft phase adjuster according to an embodiment of the present application.

Fig. 5 shows a schematic sectional view of a partial structure of the camshaft phase adjuster in the first split flow mode according to an embodiment of the present application.

Fig. 6 shows a schematic sectional view of a partial structure of the camshaft phase adjuster in the second split flow mode according to an embodiment of the present application.

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

Detailed ways

The implementation manner of the present application will be further described in detail below with reference to the drawings and embodiments. The detailed description and drawings of the following embodiments are used to illustrate the principles of the application, but not to limit the scope of the application, that is, the application is not limited to the described embodiments.

In the description of this application, it should be noted that, unless otherwise specified, the meaning of "plurality" is more than two; the orientation or positional relationship indicated by the terms "inside", "outside" and so on are only for the convenience of describing the application and simplified descriptions, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operate in a specific orientation, and thus should not be construed as limiting the application. In addition, the terms "first", "second", etc. are used for descriptive purposes only and should not be construed as indicating or implying relative importance. "Vertical" is not strictly vertical, but within the allowable range of error. "Parallel" is not strictly parallel, but within the allowable range of error.

The orientation words appearing in the following description are the directions shown in the figure, and do not limit the specific structure of the application. In the description of this application, it should also be noted that, unless otherwise clearly specified and limited, the terms "installation", "connection", and "connection" should be interpreted in a broad sense, for example, it can be a fixed connection or a flexible connection. Disassembled connection, or integral connection; it can be directly connected or indirectly connected through an intermediary. Those of ordinary skill in the art can understand the specific meanings of the above terms in this application depending on the specific circumstances.

In order to better understand the present application, the following describes the embodiment of the present application with reference to FIG. 2 to FIG. 6 .

As shown in FIG. 2 to FIG. 6 , the camshaft phase adjuster 100 is connected to the camshaft 1 to adjust the rotational phase of the camshaft 1 , thereby controlling the early/retarded opening and closing of valves connected to the camshaft 1 . Exemplarily, the camshaft phase adjuster 100 is connected to one side of the camshaft 1 by bolts or directly welded to one side of the camshaft 1 . The camshaft phaser 100 includes a stator 10 , a rotor 20 and a center valve 30 .

The stator 10 includes a base body 11 , a plurality of bosses 12 arranged at intervals in the circumferential direction and protruding radially inward, and a plurality of teeth 13 arranged in the circumferential direction and extending radially outward. A cavity 14 is formed between two adjacent bosses 12 . Usually, the stator 10 is connected to the crankshaft of the engine through a sprocket meshing with the teeth 13 .

The rotor 20 is coaxially sleeved in the stator 10 and can rotate relative to the stator 10 driven by the central valve 30 . The rotor 20 has a body 21 and a plurality of blades 22 fixed to the body 21 . A plurality of vanes 22 are arranged at intervals in the circumferential direction and extend radially outwards into the chamber 14 formed by two adjacent bosses 12 of the stator 10 to divide the chamber into a first hydraulic chamber 141 and a second hydraulic chamber 141 . hydraulic chamber 142 . Thus, the stator 10 and the rotor 20 jointly form the first hydraulic chamber 141 and the second hydraulic chamber 142 .

As shown in FIG. 4 , the rotor 20 has an inner cavity 23 and an oil inlet passage P in fluid communication with the inner cavity 23 . The inner cavity 23 is generally disposed at the radial center position of the rotor 12 and extends in the axial direction of the rotor 20 . The inner cavity 23 is substantially cylindrical. The oil inlet passage P generally extends along the axial direction of the rotor 20 . The oil inlet passage P may have a cross-sectional shape such as a circle, an ellipse, or a semicircle. The inlet of the oil inlet passage P is arranged on the side of the rotor 20 connected with the camshaft 1 and can allow the pressure fluid from the camshaft 1 to enter, while the outlet of the oil inlet passage P is exposed to the internal cavity 23 of the rotor 20 . Therefore, pressure fluid from the camshaft 1 can flow into the rotor 20 via the oil inlet passage P of the rotor 20 .

The number of oil inlet passages P may be multiple, and the plurality of oil inlet passages P are arranged at intervals along the circumference of the rotor 20 . Preferably, a plurality of oil inlet passages P are evenly arranged at intervals along the circumferential direction of the rotor 20 .

As shown in FIG. 4 , a first oil distribution channel A and a second oil distribution channel B are also formed in the rotor 20 . The first oil distribution passage A generally extends radially along the body 21 of the rotor 20, and the inlet of the first oil distribution passage A is exposed to the internal cavity 23 of the rotor 20, and the outlet of the first oil distribution passage A is exposed to the first hydraulic pressure. Room 141. Therefore, the first oil distribution passage A is in fluid communication with the first hydraulic chamber 141 but not in fluid communication with the second hydraulic chamber 142 . The second oil distribution passage B extends radially substantially along the body 21 of the rotor 20, and the inlet of the second oil distribution passage B is exposed to the inner cavity 23 of the rotor 20, and the outlet of the second oil distribution passage B is exposed to the second hydraulic chamber 142 . Therefore, the second oil distribution passage B is in fluid communication with the second hydraulic chamber 142 but not in fluid communication with the first hydraulic chamber 141 . In addition, the inlet of the first oil distribution passage A and the inlet of the second oil distribution passage B are disposed at positions different from the outlet of the oil inlet 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 disposed at positions different from the outlet of the oil inlet passage P in the circumferential direction of the rotor 20 . In other words, the oil inlet passage P does not extend to any position of both the first oil distribution passage A and the second oil distribution passage B. As shown in FIG.

Further, the inner cavity 23 includes a groove 24 recessed from the inner peripheral side of the inner cavity 23 , and the outlet of the oil inlet passage P is exposed to the groove 24 , thereby being exposed to the inner cavity 23 . The groove 24 may be annular. Of course, in other embodiments, the number of grooves 24 may be multiple, and the plurality of grooves 24 may be distributed at intervals along the circumference of the rotor 20, as long as it can expose the outlet of the oil inlet passage P to the internal cavity 23 That's it. The groove 24 can accommodate a part of the pressure fluid flowing in from the oil inlet passage P, thereby improving the hydrodynamic performance of the pressure fluid during the movement of the central valve 30 . As shown in FIG. 4 , the oil inlet passage P and the groove 24 form an L-shaped oil passage, whereby the pressure fluid entering the oil inlet passage P enters the inner cavity 23 through the inner peripheral side of the inner 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 disposed at a position between the inlet of the first oil distribution passage A and the inlet of the second oil distribution passage B along the axial direction of the rotor 20 . Therefore, the outlet of the oil inlet passage P is disposed at a position between the inlet of the first oil distribution passage A and the inlet of the second oil distribution passage B along the axial direction of the rotor 20 .

The central valve 30 is installed in the internal cavity 23 of the rotor 20, and can move in the internal cavity 23 along the axial direction of the rotor 20, so as to divide the pressure fluid flowing into the rotor 20, thereby controlling the relative flow of the rotor 20 to the stator. 10 spins. Specifically, when the central valve 30 moves axially in the internal cavity 23, the oil inlet passage P can be selectively connected with the first hydraulic chamber 141 and the first hydraulic chamber 141 by means of different positions of the central valve 30 in the internal cavity 23. The second hydraulic chamber 142 is in fluid communication, thereby guiding the pressurized fluid entering the rotor 20 to the first hydraulic chamber 141 or the second hydraulic chamber 142 , thereby controlling the rotation of the rotor 20 relative to the stator 10 .

Therefore, the camshaft phase adjuster 100 according to the embodiment of the present application can reduce the number of components, simplify the overall structure, and simplify assembly by directly disposing the central valve 30 in the inner cavity 23 of the rotor 20 . In addition, the pressure fluid can flow into the internal cavity 23 by providing the oil inlet passage P communicating with the internal cavity 23 on the rotor 20, and at the same time cooperate with the reciprocating movement of the central valve 30 in the internal cavity 23 to realize pressure control. The effect of fluid splitting, which can replace the oil channel splitting bushing in the prior art, can further reduce the number of parts and simplify the overall structure, thereby reducing the manufacturing cost of the camshaft phase adjuster 100 .

According to an exemplary embodiment of the present invention, the camshaft phase adjuster 100 may have two modes, namely, 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 141 via the first oil split passage A and not in fluid communication with the second hydraulic chamber 142 . In the second flow distribution mode, the oil inlet passage P is in fluid communication with the second hydraulic chamber 142 via the second oil distribution passage B and not in fluid communication with the first hydraulic chamber 141 . Therefore, when the central valve 30 moves axially in the inner cavity 23, the camshaft phase adjuster 100 can be switched between the first split mode and the second split mode by means of different positions of the central valve 30, thereby entering The pressure fluid of the rotor 20 is selectively guided into the first hydraulic chamber 141 and the second hydraulic chamber 142 , thereby controlling the rotation of the rotor 20 relative to the stator 10 .

Preferably, the camshaft phase adjuster 100 can also have a third mode, that is, a holding mode. In the holding mode, the oil inlet passage P is neither in fluid communication with the first hydraulic chamber 141 via the first oil distribution passage A, nor It is in fluid communication with the second hydraulic chamber 142 via the second oil distribution passage B. At this time, since the pressurized fluid neither enters into the first hydraulic chamber 141 nor enters into the second hydraulic chamber 142 , the position of the rotor 20 relative to the stator 10 can be kept unchanged.

As shown in FIGS. 5 and 6 , the central valve 30 includes a piston 31 and an elastic member 32 . The piston 31 is inserted into the inner cavity 23 from an end of the inner cavity 23 away from the camshaft 1 and can move in the inner cavity 23 in the axial direction of the rotor 20 under the action of, for example, an electromagnet. An electromagnet (not shown) is mounted on the end of the piston 31 away from the elastic member 32 . The piston 31 is substantially in the shape of a hollow cylinder. The piston 31 is formed with first protrusions 311 and second protrusions 312 spaced along the axial direction of the rotor 20. The first protrusion 311 and the second protrusion 312 respectively extend radially outward from the outer peripheral surface of the piston 31 toward the inner peripheral side of the inner cavity 23 . The first protrusion 311 corresponds to the first oil distribution channel A, and the second protrusion 312 corresponds to the second oil distribution channel B. Therefore, when the piston 31 moves axially in the inner cavity 23 so that the camshaft phase adjuster 100 is in the first split flow mode, the second protrusion 312 is located between the groove 24 and the second oil split passage B in the axial direction. The position between the inlets thereby restricts the pressure fluid from flowing into the second hydraulic chamber 142 via the second oil distribution channel B. When the piston 31 moves axially in the inner cavity 23 so that the camshaft phase adjuster 100 is in the second split flow mode, the first protrusion 311 is axially located between the groove 24 and the inlet of the first oil split passage A position, thereby restricting the pressure fluid from flowing into the first hydraulic chamber 141 through the first oil distribution passage A. In addition, when the piston 31 moves axially in the internal cavity 23 so that the camshaft phase adjuster 100 is in the holding mode, the first protrusion 311 is axially located between the groove 24 and the inlet of the second oil distribution passage B At the same time, the second protrusion 312 is located at the position between the groove 24 and the inlet of the first oil distribution channel A in the axial direction, thereby preventing the pressure fluid from entering the first hydraulic chamber 141 and the second hydraulic chamber 142, while The position of the rotor 20 relative to the stator 10 remains unchanged.

The piston 31 also includes a groove 313 formed between the first protrusion 311 and the second protrusion 312 , the groove 313 corresponds to the groove 24 of the inner cavity 23 and is in fluid communication with the groove 24 of the inner cavity 23 . Therefore, the groove 313 can also accommodate a part of the pressure fluid flowing in from the oil inlet passage P, so as to improve the hydrodynamic performance of the pressure fluid during the movement of the piston 31 .

In addition, as shown in FIG. 5 and FIG. 6, a circular arc transition portion is formed between the first protrusion 311 and the groove 313 and/or the second protrusion 312 and the groove 313, thereby reducing stress concentration problems caused by processing, Thereby prolonging the service life of the piston 31 . The piston 31 further includes an axially extending central hole 314 and a through hole 315 radially penetrating the piston 31 and communicating with the central hole 314 . The through hole 315 is used to communicate the pressurized fluid in the internal cavity 23 with the external environment.

The elastic member 32 is connected to the piston 31 to exert elastic force on the piston 31 in the axial direction so as to reset the piston 31 . Specifically, the elastic member 32 is disposed between the piston 31 and an end of the inner cavity 23 close to the camshaft 23 . Thus, when the elastic member 32 is compressed under the action of the electromagnet, it can exert an elastic force on the piston 31 so that the piston 31 returns to its original position. In one example, the elastic member 32 is a spring.

Therefore, when the camshaft phase adjuster 100 works, the electromagnet can push the piston 31 in the axial direction according to the control signal sent by the engine control system, so that the piston 31 selectively opens and closes the first valve leading to the first hydraulic chamber 141. The oil distribution channel A and the second oil distribution channel B leading to the second hydraulic chamber 142 to control the flow of pressure fluid entering the first hydraulic chamber 141 and the second hydraulic chamber 142, thereby adjusting the rotation angle of the rotor 20 relative to the stator 10 , so that the valve opens earlier or later.

The working principle of the camshaft phase adjuster 100 will be described below with reference to FIGS. 5 and 6 .

FIG. 5 shows a schematic diagram of the camshaft phaser 100 in the first split mode. When the camshaft phase adjuster 100 is in the first split flow mode, the piston 31 is in the first position (ie the left side position), and the elastic member 32 is in the first compressed state. At this time, the first protrusion 311 is located on the left side of the inlet of the first oil distribution passage A so that the outlet of the oil inlet passage P is in fluid communication with the inlet of the first oil distribution passage A (not shown), so as to allow The pressure fluid entering the rotor 20 enters the first hydraulic chamber 141 through the first oil distribution passage A, and the second protrusion 312 is located at a position between the groove 24 and the inlet of the second oil distribution passage B in the axial direction. , thereby restricting the pressure fluid from flowing into the second hydraulic chamber 142 via the second oil distribution passage B. Preferably, the second protrusion 312 may be partially located at the entrance of the second oil distribution passage B. As shown in FIG. The pressurized fluid entering the first hydraulic chamber 141 will force the rotor 20 to rotate (clockwise) toward the direction of pressing the second hydraulic chamber 142, and with such rotation, the pressurized fluid in the second hydraulic chamber 142 will move along the second hydraulic chamber 142. The oil distribution channel B flows into the central hole 314 of the piston 34 , and then flows out of the piston 34 through the through hole 315 .

Similarly, FIG. 6 shows a schematic diagram of the camshaft phaser 100 in the second split mode. When the camshaft phase adjuster 100 is in the second split mode, the piston 31 is in the second position (ie, the right position), and the elastic member 32 is in the second compressed state, wherein the compression amount of the elastic member 32 in the second compressed state is greater than the compression amount of the elastic member 32 in the first compressed state. At this time, the second protrusion 312 is located on the right side of the inlet of the second oil distribution passage B so that the outlet of the oil inlet passage P is in fluid communication with the inlet of the second oil distribution passage B to allow the rotor 20 to enter through the oil inlet passage P. The pressurized fluid enters the second hydraulic chamber 142 through the second oil distribution channel B, and the first protrusion 311 is located at a position between the groove 24 and the inlet of the first oil distribution channel A in the axial direction, thereby limiting the pressure Fluid flows into the first hydraulic chamber 141 through the first oil distribution passage A. Preferably, the first protrusion 311 may be partially located at the entrance of the first oil distribution channel A. Referring to FIG. The pressure fluid entering the second hydraulic chamber 142 will force the rotor 20 to rotate toward the direction (counterclockwise) that squeezes the first hydraulic chamber 141, and with such rotation, the pressure fluid in the first hydraulic chamber 141 will move along the first The oil distribution channel A flows into the central hole 314 of the piston 34 , and then flows out of the piston 34 through the through hole 315 .

Figures 5 and 6 only show two limit positions of the piston 31, of course the piston 31 according to the embodiment of the application can have other positions different from these two limit positions according to actual needs, so as to adjust the rotor 20 more accurately Relative to the rotation angle of the stator 10, the opening of the valve is determined to be advanced or delayed according to the operating conditions of the engine. For example, the camshaft phase adjuster 100 according to the embodiment of the present invention can be in the holding mode, at this time, the first protrusion 311 is just located at the entrance of the first oil distribution channel A in the axial direction, thereby blocking the first oil distribution channel A. The inlet of passage A, so that the pressure fluid is prohibited from flowing into the first hydraulic chamber 141 through the first oil distribution passage A, and the pressure fluid in the first hydraulic chamber 141 is prohibited from flowing out through the first oil distribution passage A, so as to maintain the first hydraulic pressure. The capacity of the pressure fluid in the chamber 141 remains unchanged; the second protrusion 312 is located at the entrance of the second oil distribution channel B in the axial direction, thereby blocking the entrance of the second oil distribution channel B, thereby prohibiting the pressure fluid from passing through the second oil distribution channel B. The oil distribution passage B flows into the second hydraulic chamber 142 while the pressure fluid in the second hydraulic chamber 142 is prohibited from passing through the second oil distribution passage B to keep the capacity of the pressure fluid in the second hydraulic chamber 142 unchanged. That is to say, in the holding mode, the oil inlet passage P is neither in fluid communication with the first oil distribution passage A nor with the second oil distribution passage B, and at the same time, the first hydraulic chamber 141 and the second hydraulic chamber 142 are not in fluid communication. It will communicate with the external environment through the first oil distribution channel A and the second oil distribution channel B respectively, so as to ensure that the respective pressure fluid capacities of the first hydraulic chamber 141 and the second hydraulic chamber 142 remain unchanged, so that the rotor 20 can be maintained The position relative to the stator 10 remains unchanged.

While the present application has been described with reference to a preferred embodiment, various modifications may be made thereto and equivalents may be substituted for parts thereof without departing from the scope of the present application, in particular, as long as there are no structural conflicts , the technical features mentioned in each embodiment can be combined in any way. The present application is not limited to the specific embodiments disclosed herein, but includes all technical solutions falling within the scope of the claims.

Claims

A camshaft phase adjuster (100), which is connected to a camshaft (1) to adjust the rotational phase of the camshaft (1), the camshaft phase adjuster (100) includes a stator (10), a rotor ( 20) and a central valve (30), the rotor (20) is coaxially sleeved in the stator (10) and can rotate relative to the stator (10), wherein,

The rotor (20) has an inner cavity (23) and an oil inlet passage (P) in fluid communication with the inner cavity (23), the pressure fluid from the camshaft (1) passes through the rotor (20 ) of the oil inlet channel (P) flows into the rotor (20), the central valve (30) is installed in the inner cavity (23) of the rotor (20), and can be in the move in the inner cavity (23) along the axial direction of the rotor (20), so as to divide the pressure fluid flowing into the rotor (20), so as to control the rotor (20) relative to the The rotation of the stator (10).
The camshaft phase adjuster (100) according to claim 1, wherein

The number of the oil inlet passages (P) is multiple, the plurality of the oil inlet passages (P) are arranged at intervals along the circumference of the rotor (20), and each of the oil inlet passages (P) is arranged along the circumference of the rotor (20). said axial extension.
The camshaft phase adjuster (100) according to claim 1, wherein

The stator (10) and the rotor (20) jointly form a first hydraulic chamber (141) and a second hydraulic chamber (142), and

When the central valve (30) moves along the axial direction in the inner cavity (23), the oil inlet passage (P) can be selectively connected with the first hydraulic chamber (141) and the The second hydraulic chamber (142) is in fluid communication.
The camshaft phaser (100) according to claim 3, wherein

The rotor (20) has a first oil distribution passage (A) in fluid communication with the first hydraulic chamber (141) and a second oil distribution passage (B) in fluid communication with the second hydraulic chamber (142) ,and

When the central valve (30) moves in the axial direction in the inner cavity (23), the camshaft phase adjuster (100) can communicate with the first oil distribution passage (A) The first split mode in which the first hydraulic chamber (141) is not in fluid communication with the second hydraulic chamber (142) is connected to the oil inlet passage (P) via the second oil distribution passage (B) Switching between a second split mode in fluid communication with the second hydraulic chamber (142) and not in fluid communication with the first hydraulic chamber (141).
The camshaft phaser (100) according to claim 3, wherein

When the central valve (30) moves along the axial direction in the internal cavity (23), the camshaft phase adjuster (100) also has the oil inlet passage (P) neither with the A holding mode in which the first hydraulic chamber (141) is not in fluid communication with the second hydraulic chamber (142).
The camshaft phase adjuster (100) according to claim 4, wherein

The outlet of the oil inlet passage (P) is disposed at a different position from the inlets of the first oil separation passage (A) and the second oil distribution passage (B).
The camshaft phase adjuster (100) according to claim 4, wherein

The inner cavity (23) has a groove (24) recessed from the inner peripheral side of the inner cavity (23), and the outlet of the oil inlet channel (P) is exposed to the groove (24). ), and the groove (24) is arranged at a position between the inlet of the first oil distribution passage (A) and the inlet of the second oil distribution passage (B) along the axial direction.
The camshaft phase adjuster (100) according to claim 4, wherein

The central valve (30) is inserted into the inner cavity (23) from an end of the inner cavity (23) far away from the camshaft (1) and can be inserted in the inner cavity (23) along the axially movable piston (31), the piston (31) comprising a first protrusion (311) and a second protrusion (312) spaced along the axial direction, and

When the camshaft phase adjuster (100) is in the first split flow mode, the second protrusion (312) restricts the pressure fluid from flowing into the first oil split passage (B) in the second hydraulic chamber (142), and when the camshaft phase adjuster (100) is in the second split mode, the first protrusion (311) restricts the pressure fluid from passing through the first oil split passage (A) to flow into the first hydraulic chamber (141).
The camshaft phase adjuster (100) according to claim 8, wherein

The inner cavity (23) has a groove (24) recessed from the inner peripheral side of the inner cavity (23), and the outlet of the oil inlet passage (P) is exposed to the groove (24), so The piston (31) further includes a recess (313) arranged on the first protrusion (311) and the second protrusion (312), and the recess (313) corresponds to the groove (24).
The camshaft phase adjuster (100) according to claim 8, wherein

The central valve (30) also includes an elastic member ( 32).