CN111485969A

CN111485969A - Camshaft phase adjuster

Info

Publication number: CN111485969A
Application number: CN201910081879.XA
Authority: CN
Inventors: 全婷; 菅宝玉
Original assignee: Schaeffler Technologies AG and Co KG
Current assignee: Schaeffler Holding China Co Ltd
Priority date: 2019-01-28
Filing date: 2019-01-28
Publication date: 2020-08-04

Abstract

The invention relates to a camshaft phase adjuster. This camshaft phase regulator is used for adjusting camshaft's rotation phase place, and it includes stator, rotor and hydrovalve, and the coaxial cover of rotor is established in the hydrovalve outside, and the hydrovalve control rotor is for the rotation of stator, and the hydrovalve has valve body, case and spring, and the case is settled in the valve body and through the spring butt in the valve body towards the one end of the axle head of camshaft, and wherein, the valve body is direct to be connected with the rotor is antitorque, and the rotor is antitorque with the axle head and is connected. The camshaft phase adjuster is simple in structure and easy to assemble.

Description

Camshaft phase adjuster

Technical Field

The invention relates to the technical field of engines. In particular, the present invention relates to a camshaft phase adjuster for a variable valve timing system of an engine.

Background

In a variable valve timing system of an automobile engine, a hydraulic valve assembly and a camshaft phase adjuster assembly are separately included, the hydraulic valve assembly is installed in a rotor of the phase adjuster, the camshaft is installed in the phase adjuster, a hydraulic valve is connected with the camshaft through threads on the end face of the rotor, and a hydraulic valve body contains working parts of the hydraulic valve inside the valve body. The assembling mode has higher precision requirement on the matching between the camshaft and the phase adjuster, and has more parts and complex oil path design.

Disclosure of Invention

Therefore, the technical problem to be solved by the invention is to provide a camshaft phase adjuster which is simple in structure and easy to assemble.

The above-mentioned technical problem is solved by a camshaft phase adjuster according to the present invention. The camshaft phase regulator comprises a stator, a rotor and a hydraulic valve, wherein the rotor is coaxially sleeved on the outer side of the hydraulic valve, the hydraulic valve controls the rotor to rotate relative to the stator, the hydraulic valve is provided with a valve body, a valve core and a spring, the valve core is arranged in the valve body and abuts against one end of the valve body, facing to the shaft end of a camshaft, through the spring, the valve body is directly connected with the rotor in an anti-torsion mode, and the rotor is connected with the shaft end of the camshaft. Because the hydraulic valve is not required to be directly connected with the camshaft through threads, the hydraulic valve can be directly integrated in the camshaft phase adjuster, and the structure of the timing system can be greatly simplified. Preferably, the rotor is fixedly connected to the shaft end of the camshaft by means of at least one bolt or by means of welding. The connecting mode is very simple, the assembling and positioning are convenient, and the matching precision between the camshaft phase adjuster and the camshaft can be reduced.

According to a preferred embodiment of the present invention, a circumferentially extending valve chamber is formed between the valve body and the spool, and an oil drain groove is formed in the rotor, from which oil drain groove the pressure fluid of the hydraulic valve enters the valve chamber. Because the hydraulic valve is directly integrated in the rotor, an oil guide groove of the hydraulic valve can be directly arranged in the rotor, and the system structure is further simplified.

According to another preferred embodiment of the invention, a one-way valve is arranged between the valve body and the shaft end, from which one-way valve the pressure fluid enters the oil sump. In addition, the valve body is stopped in the direction away from the spring through a clamping ring clamped in the rotor. The check valve controls the pressure fluid flowing into the oil guide groove to prevent the pressure fluid from flowing back, and the check valve is directly pressed on one end of the valve body and matched with the snap ring on the other end of the valve body to axially position the hydraulic valve. Preferably, the check valve is press-fitted in the rotor by a plurality of pins. The pins allow the non-return valve to be fixed to the rotor in a simple and reliable manner.

According to another preferred embodiment of the present invention, the valve body is formed with an inlet corresponding to an outlet of the oil drain groove, and the pressure fluid enters the valve chamber from the inlet. Preferably, a plurality of oil drainage grooves are formed in the rotor and are spaced apart in the circumferential direction, a plurality of inlets are formed in the valve body and are spaced apart in the circumferential direction, and the plurality of oil drainage grooves correspond to the plurality of inlets one to one. The pressure fluid enters from the oil guide groove in the rotor and directly enters the valve chamber through the inlet on the valve body, and the oil path structure is greatly simplified.

According to another preferred embodiment of the invention, the valve body is formed with a first outlet and a second outlet, the first outlet being closer to an end of the valve body facing away from the shaft end than the inlet, the second outlet being closer to an end of the valve body facing towards the shaft end than the inlet, and the second outlet being not on the same axial extension as the inlet. The first outlet and the second outlet are respectively positioned at two axial sides of the inlet, and when the valve core moves axially, the valve chamber is driven to move axially, so that the inlet is communicated with the first outlet or the second outlet, hydraulic fluid flows into different hydraulic cavities, and the rotor is driven to rotate towards different directions relative to the stator. The second outlet and the inlet are not on the same axial extension line, namely the second outlet and the inlet are staggered along the circumferential direction, so that the second outlet avoids the position of an oil guide groove communicated with the inlet in the rotor. Further preferably, the valve body has a plurality of first outlets and a plurality of second outlets formed thereon and spaced apart in the circumferential direction.

Drawings

The invention is further described below with reference to the accompanying drawings. Identical reference numbers in the figures denote functionally identical elements. Wherein:

FIG. 1 is a cross-sectional view of a camshaft phase adjuster according to an embodiment of the present invention;

FIG. 2 is an enlarged view of a portion of the cross-section of FIG. 1; and

FIG. 3 is a partially enlarged view of another cross section of a camshaft phase adjuster according to an embodiment of the present invention.

Detailed Description

Hereinafter, a specific embodiment of a camshaft phase adjuster according to the present invention will be described with reference to the accompanying drawings. The following detailed description and drawings are included to illustrate the principles of the invention, which is not to be limited to the preferred embodiments described, but is to be defined by the appended claims.

Fig. 1 shows a sectional view of a camshaft phase adjuster according to an embodiment of the invention. As shown in fig. 1, the camshaft phase adjuster includes a stator 1, a rotor 2, and a hydraulic valve. The stator 1 is coaxially sleeved on the outer side of the rotor 2, the rotor 2 is coaxially sleeved on the outer side of the hydraulic valve, and the rotor 2 can rotate relative to the stator 1 under the driving of the hydraulic valve. The shaft end 3 of the camshaft abuts against one side end face of the camshaft phase adjuster, and the bolt 12 penetrates the rotor 2 from the other side end face of the phase adjuster and is inserted into a corresponding hole of the shaft end 3, thereby fixedly connecting the rotor of the phase adjuster with the camshaft. In the present exemplary embodiment, a total of four bolts 12 spaced apart in the circumferential direction are provided in order to ensure a stable rotationally fixed connection of the camshaft to the rotor 2, but other numbers of bolts 12 can also be provided, without the invention being restricted thereto. In addition, the camshaft and the rotor 2 can also be connected in other ways, for example by welding, as long as a direct torque-proof connection of the camshaft and the rotor 2 is ensured.

The hydraulic valve is arranged coaxially inside the rotor 2. The hydraulic valve comprises a valve body 4, a valve core 5 and a spring 6. The valve body 4 and the valve body 5 are cylindrical, and the valve body 4 is mounted in the rotor 2 so as to be rotationally fixed. One end of the valve body 4 facing the shaft end 3 is closed, the other end of the valve body is opened, the open end is pressed with the snap ring 10 and is axially abutted against the rotor 2 through the snap ring 10, and the closed end is pressed with the one-way valve 9 and is abutted against the shaft end 3 through the one-way valve 9. As shown in fig. 3, the check valve 9 has a plurality of pins 11, and the pins 11 are press-fitted into the rotor 2, thereby fixing the check valve 9 to the rotor 2. The one-way valve 9 and the snap ring 10 together define the axial position of the valve body 4. The valve spool 5 is arranged in the valve body 4 and is abutted against the closed end of the valve body 4 by the spring 6. Outside the end of the hydraulic valve facing away from the shaft end 3, an electromagnet or other force application mechanism (not shown) is provided, the electromagnet can generate an axial magnetic force on the valve core 5, and the valve core 5 can move axially in the valve body 4 under the combined action of the elastic force of the spring 6 and the magnetic force of the electromagnet. A circumferentially extending valve chamber 7 is formed between the valve body 4 and the spool 5, in which valve chamber 7 the inner wall of the valve body 4 is radially spaced from the outer wall of the spool 5, while at both axial ends of the valve chamber 7 the inner wall of the valve body 4 forms a contact seal with the outer wall of the spool 5, so that the valve chamber 7 forms a relatively independent hydraulic fluid receiving space. When the spool 5 moves axially within the valve body 4, the valve chamber 7 also moves axially therewith.

Fig. 2 is a partially enlarged view of the embodiment of fig. 1, showing hydraulic fluid flow passages of the phase adjuster according to the present embodiment. As shown in fig. 2, a plurality of oil sumps 8 are formed in the rotor 2, each oil sump 8 extending axially inward from an end surface of the rotor 2 abutting the check valve 9 and communicating at the other end with the valve chamber 7 through a corresponding inlet port P (port P) in the valve body 4. In the present embodiment, four circumferentially spaced oil drainage grooves 8 are formed conformally on the rotor 2, and four circumferentially spaced P ports are also formed at corresponding positions on the valve body 4. However, the oil drainage grooves 8 and the P ports may be provided in other numbers as long as they correspond to each other, and the present invention is not limited thereto. A plurality of first outlet ports a (ports a) and a plurality of second outlet ports B (ports B) are formed in the valve body 4, wherein the ports a are circumferentially spaced apart on a side of the ports P facing away from the shaft end 3, and the ports B are circumferentially spaced apart on a side of the ports P facing toward the shaft end 3. The circumferential position of each port B and the circumferential position of the port P are mutually staggered, namely the ports B and the ports P are not positioned on the same axial extension line, so that the ports B are prevented from being communicated due to the overlapping of the positions of the ports B and the oil guide grooves 8. The ports a and B correspond to different flow passages in the rotor 2, and are communicated with a cavity a and a cavity B (not shown) formed between the stator 1 and the rotor 2. When the valve core 5 moves away from the shaft end 3, the valve chamber 7 is communicated with the port P and the port A at the same time, hydraulic fluid flows into the oil guide groove 8 from the one-way valve 9 in one way, enters the valve chamber 7 through the port P and flows into the corresponding cavity A between the stator 1 and the rotor 2 through the port A, and meanwhile, the hydraulic fluid in the cavity B can flow into the inner side of the valve core 5 from the corresponding port B and is discharged from a hole at the end part of the valve core 5, so that the rotor 2 is pushed to rotate relative to the stator 1 in one direction. When the spool 5 moves close to the shaft end 3, the valve chamber 7 is communicated with the port P and the port B at the same time, the hydraulic fluid entering the valve chamber 7 flows into the corresponding cavity B between the stator 1 and the rotor 2 from the port B, and the hydraulic fluid in the cavity A can be directly discharged out of the left end of the valve body 4 from the corresponding port A, so that the rotor 2 is pushed to rotate relative to the stator 1 in the other opposite direction. Thus, the phase of the camshaft is adjusted.

Although possible embodiments have been described by way of example in the above description, it should be understood that numerous embodiment variations exist, still by way of combination of all technical features and embodiments that are known and that are obvious to a person skilled in the art. It should also be appreciated that the exemplary embodiment or exemplary embodiments are only examples, and are not intended to limit the scope, applicability, or configuration of the invention in any way. From the foregoing description, one of ordinary skill in the art will more particularly provide a technical guide to convert at least one exemplary embodiment, wherein various changes may be made, particularly in matters of function and structure of the components described, without departing from the scope of the following claims.

List of reference numerals

1 stator

2 rotor

3 shaft end

4 valve body

5 valve core

6 spring

7 valve chamber

8 draw oil groove

9 one-way valve

10 clasp

11 pin

12 bolt

P inlet (P port)

A first outlet (A port)

B second outlet (B port)

Claims

1. A camshaft phase adjuster is used for adjusting the rotation phase of a camshaft and comprises a stator (1), a rotor (2) and a hydraulic valve, wherein the rotor (2) is coaxially sleeved on the outer side of the hydraulic valve, the hydraulic valve controls the rotor (2) to rotate relative to the stator (1), the hydraulic valve is provided with a valve body (4), a valve core (5) and a spring (6), the valve core (5) is arranged in the valve body (4) and is abutted against one end, facing to a shaft end (3) of the camshaft, of the valve body (4) through the spring (6),

it is characterized in that the preparation method is characterized in that,

the valve body (4) is directly connected with the rotor (2) in a torsion-proof manner, and the rotor (2) is connected with the shaft end (3) in a torsion-proof manner.

2. A camshaft phase adjuster according to claim 1, characterized in that the rotor (2) is fixedly connected to the shaft end (3) by means of at least one bolt (12) or by means of welding.

3. A camshaft phase adjuster according to claim 1, characterized in that a circumferentially extending valve chamber (7) is formed between the valve body (4) and the spool (5), an oil drain groove (8) is formed in the rotor (2), and the pressure fluid of the hydraulic valve enters the valve chamber (7) from the oil drain groove (8).

4. A camshaft phase adjuster according to claim 3, characterized in that a one-way valve (9) is arranged between the valve body (4) and the shaft end (3), from which one-way valve (9) the pressure fluid enters the oil drain groove (8).

5. A camshaft phase adjuster as claimed in claim 4, characterized in that the non-return valve (9) is press-fitted in the rotor (2) by means of a plurality of pins (11).

6. A camshaft phase adjuster as claimed in claim 4, characterized in that the valve body (4) is stopped in the direction away from the spring (6) by means of a snap ring (10) which snaps into the rotor (2).

7. A camshaft phase adjuster according to claim 4, wherein an inlet (P) corresponding to an outlet of the oil guide groove (8) is formed in the valve body (4), and the pressure fluid enters the valve chamber (7) from the inlet (P).

8. A camshaft phase adjuster according to claim 7, wherein a plurality of the oil introducing grooves (8) are formed in the rotor (2) so as to be spaced apart in the circumferential direction, a plurality of the inlet ports (P) are formed in the valve body (4) so as to be spaced apart in the circumferential direction, and a plurality of the oil introducing grooves (8) correspond one-to-one to the plurality of the inlet ports (P).

9. A camshaft phase adjuster as claimed in claim 7, characterized in that the valve body (4) is formed with a first outlet (A) and a second outlet (B), the first outlet (A) being closer to the end of the valve body (4) facing away from the shaft end (3) than the inlet (P), the second outlet (B) being closer to the end of the valve body (4) facing towards the shaft end (3) than the inlet (P), and the second outlet (B) not being on the same axial extension as the inlet (P).

10. A camshaft phase adjuster as claimed in claim 9, characterized in that the valve body (4) has formed thereon a plurality of the first outlet (a) and a plurality of the second outlet (B) which are circumferentially spaced apart.