JP3450007B2 - Hydraulic control device - Google Patents

Description

Description: BACKGROUND OF THE INVENTION The invention starts from a hydraulic control device for rotating the camshaft of an internal combustion engine of the type premised on the preamble of claim 1. In such a known control device, in particular, the pump and the magnet valve are arranged externally, which is particularly cumbersome with regard to the required conduit connections and requires considerable production costs (German Patent Publication DE 3247116). issue).

Advantages of the Invention On the other hand, the hydraulic control device according to the present invention having the features of claim 1 is extremely compact in structure and can be installed extremely easily in the internal combustion engine or in the engine room of the internal combustion engine. It has the advantage of Further advantages of the invention are apparent from claims 2 and below.

Drawings Embodiments of the present invention are described by the following description and drawings. FIG. 1 shows a longitudinal section of the first embodiment, and FIG. 2 shows II of FIG.
5 shows a cross section taken along line II, FIG. 3 also shows a vertical cross section of the second embodiment, FIG. 4 shows a modification of the second embodiment, and FIG.
Shows a partial longitudinal section of the third embodiment only, and FIG. 6 shows a front view of details of the third embodiment.

DESCRIPTION OF THE PREFERRED EMBODIMENTS In FIG. 1, the reference numeral 10 designates the end of a camshaft, which camshaft serves to operate the valve of an internal combustion engine. An elongated cylindrical central member 11 is firmly screwed into the end of the camshaft, and the axis of the central member extends coaxially with the axis of the camshaft. At approximately the center of the central member 11, a connecting member 12 is slidably supported on the outer periphery thereof, and the connecting member has a helical spacer 13 on the outer periphery and an inner periphery thereof at the end opposite to the cam shaft. It also has a hasb 14 in the same plane. Hasuba 14 is the central member
While it is engaged with the hasbah 15 on the outer periphery of 11, the hasbah 13
Is the inner circumference of the extension 17 of the chain wheel 18
16 engaged. The camshaft 10 is supported in a camshaft bearing 20 which is constructed at a suitable position of the internal combustion engine, for example. As can be seen from the above, the central member 11 rotates with the cam shaft, and of course, the chain wheel 18 driven by the crankshaft of the internal combustion engine also rotates, and the connecting member 12 also rotates. The connecting member has a deep groove 21 extending in the longitudinal direction, in which a push spring 22 is arranged, which on the one side is at the bottom of the connecting member and on the other side is a chain wheel.
It is supported by a cover 23 that closes the extension 17 of the 18.

A radial piston pump 26 is arranged in the notch 25 inside the chain wheel 18. This radial piston pump has a stator 27, which is rigidly connected to the camshaft bearing 20 via a pin 28. A plurality of holes 29 extending substantially in the radial direction are formed in the stator, and pistons 30 slide in the holes, and these pistons have a control ring with a circular top located outside thereof.
It is in contact with 31 and this control ring is also notched 25
It is located inside. The cylindrical notch 25 is formed eccentrically with respect to the axis of the central member 11 or the camshaft 10 in order to make the piston 30 perform a stroke motion. The control ring 31 is arranged non-rotatably by a radially inwardly extending pin 32 which projects into a dimensionally matched slit 33 in the stator 27. See FIG. 2 for this. In FIG. 2, the notch 25
It can be clearly seen that the eccentricity is formed.

The end of the central member 11, which lies in the same radial plane as the piston 30, is configured as a control pin for the radial piston pump 26 and has two mutually facing control slits extending along its circumference. 36 and 37 are provided for the high pressure side and the low pressure side. Hole for piston 30
A small hole 38 is formed in the bottom of 29, which is connected to a blind hole 39 extending laterally in the central member, which also extends longitudinally in the central member. The passage 40 is open. Second from the longitudinal passage 40
The lateral hole 41 of the above is projected and opened into the pressure chamber 43 formed between the connecting member 12 and the chain wheel 18.

A cylindrical enlarged portion 44 is formed at an end of the passage 40 on the side opposite to the camshaft 10, and a plunger 45 of a valve body 46 is located in the enlarged portion. 40 can be closed or opened. The plunger 45 has two flanges 47 and 48 in the area of the enlarged portion 44, and a vertical groove (not shown) is formed on the outer circumference of these flanges. The end of the plunger opposite the valve body 46 is fixed in the armature 50 of an electromagnet 51, which consists of a winding 52 and the associated iron core 53 in a known manner. The plunger 45 penetrates the central hole 55 of the cover 23.

When the chain wheel 18 is driven-of course the camshaft 10
The central member 11 and the connecting member also rotate-the piston 30 carries out a stroke movement. These pistons are loaded with engine hydraulic pressure through a hole or chamber 56 in the end of the camshaft, which also opens an inclined hole 57 on the end side of the central member 11. The sucked pressure medium is pushed out by the piston into the blind hole 39, the passage 40 and the lateral hole 41. This pressure medium reaches the pressure chamber 43 at the end of the connecting member 12.

When the electromagnet 51 is not energized, the carrier flow pushes the valve body 46 away from its seat, so that the pressure medium can return to the oil tank via the enlargement 44 and the lateral hole 59, which is only shown in phantom. . The pressure chamber 43 is now pressureless, so that the push spring 22 moves the connecting member 12 to the right.
The chain wheel 18 is now caused to rotate relative to the camshaft 10 by means of the above mentioned hook, so that this camshaft occupies its first position. This means "slow opening and closing" of the engine valve. By the way, when the electromagnet 51 is excited, the valve body 46
Approaches the valve seat and the carrier flow is throttled, whereby a corresponding pressure is created in the pressure chamber 43 according to the magnetic force. The rising pressure in the pressure chamber 43 now pushes the connecting member 12 into the spring 22.
Move to the left against the force of. Furthermore, this pressure forces the chain wheel 18 axially against the stator 27. This improves the sealing action for radial clearance in the stator. On the other hand, pressure relief surfaces (not shown) are mounted on the stator in order to prevent excessive pressure forces between the two parts and also against the camshaft and thus friction forces. The mitigation surface produces a particular force reduction.

In short, the generated pressure causes the connecting member 12 to move to the left against the force of the push spring 22. This causes the chain wheel 18 to rotate relative to the camshaft 10 and thus continuously create new positions in the direction of "early opening" of the intake valve. By corresponding pressure selection, in other words by corresponding current supply to the electromagnet 51, it is possible to adjust any position within the stroke range of the internal combustion engine.

When deciding the position of the control slits for suction and discharge in the central member 11, it should be noted that the relationship with the eccentric notch 25 changes during phase adjustment. Therefore, it is necessary to avoid that the sealing area of the central member seals the transfer chamber during the transfer process. Therefore, in the "slow position", the relationship between the control slits shown in FIG. 2 must be realized.

The embodiment shown in FIG. 3 differs from the embodiment according to FIG.
The connecting member-designated by 12A-is loaded in double action
In other words, there are pressure chambers on both sides thereof, designated 63 and 64. This requires some variation in the configuration of the radial piston pump-shown at 26A-the central member 11A and the solenoid valve generally shown at 65.

Not all the details of the radial piston pump 26A will be explained, but two side-by-side outlet holes 6 in the stator 27A.
7.68 and two side by side entrance holes 69 and 70 are formed. This is necessary because of the separate connection to both pressure chambers 63 and 64 via the corresponding passages 72 and 73 in the central member 11A. It is also important that the valve body 74 has two valve conical portions 75 and 76, in which case the valve conical portion 76 belongs to the high pressure passage 73. The chamber 77 at the enlarged part 71 of this high pressure passage of the central member 11A is connected to a low pressure passage 78 which extends parallel to the passage 73, this low pressure passage being on the low pressure side 80 which is connected to the oil tank. I understand. From this low-pressure passage, an inclined hole 81 (suction passage) communicates with a suction slit 82 in the central member, and discharge slits 84, 85 of the central member are located on the side facing the suction slit. What is important in this radial piston pump is that the radial piston pump must have two pistons facing each other.

The valve element 74 has a central portion, and a slit 87 is formed on the outer periphery of the central portion, and the chamber is inserted through these slits.
There is a connection from 77 to the room 88 on the opposite side.
The bush 89 continues to this, and this bush has a through-hole.
90, through which a connection to the pressure chamber 63 is made, also through a hasb. A plunger 92 is also connected to the valve element 74, and this plunger is fixed in the armature 50.

The pressure chambers 63 and 64 are loaded or unloaded depending on the position of the valve element 74. Correspondingly, the coupling member 12A is moved, which is also pivoted via its hasps--as described in the case of the exemplary embodiment according to FIG. 1--with the camshaft relative to the chain wheel 18. Excuse me. The removal of pressure from the pressure chamber 63 is achieved, for example, by the valve cone 76 seating on its valve seat, thereby connecting the chamber 88 to the low pressure passage 78 via the valve seat of the valve cone 75 and the longitudinal slit 87. When it is born. The electric current is supplied to the solenoid valve according to a specific program, for example, from an electronic control unit.

The embodiment of FIG. 4 is again a modification of the embodiment of FIG. 1, but is similar to the embodiment of FIG. This is because it also has a connecting member that is loaded in a double-acting manner. The only change was the radial piston pump-shown as 26B. This structure is more compact than that already mentioned. This is because important parts are incorporated inside and outside, in other words, they are located in one radial plane. For this reason, this embodiment is only partially shown. That is, the valve control mechanism is the same.

The important part of this altered embodiment is
This is the portion where the circular top of the piston 30 contacts. It is configured as a ring 95, which is eccentrically supported on a cylindrical extension 97 directed towards the camshaft of the chain wheel 18B and is non-rotatably connected via a pin 96 to the stator 27B. This stator is therefore supported by the cam bearing 20. In short-unlike the previous embodiments-
One part of the ring 95, the stator 27B and the connecting member 12A is 1
Located in two radial planes. This results in a particularly low volume structure. The pressure medium connection is substantially the same as in the embodiment according to FIG. 3, in other words the connecting member 12A is also of the same construction and is loaded from both sides. However, the pressure medium supply path from the engine room to the radial piston pump is configured differently. In this case, a radial hole 99 extends from the low pressure side 98 to the outside in the camshaft, and an axially extending hole 100-still in the camshaft-is connected to this radial hole, and the hole 100 is connected to the central member 11B. Inside passage
It is connected to 101, and this passage itself is an extension 97 of the chain wheel 18B.
It is connected to the suction slit 103 of the radial piston pump via an inner passage 102. The outlet side (high pressure side) will not be described. This is because it generally corresponds to the embodiment according to FIG. The function is not different from that according to the embodiment of FIG.

The embodiment according to FIGS. 5 and 6 differs significantly from the previous embodiments with respect to the transport pump. This is because an annular gear pump or G-rotor pump is used in this case. This ring gear pump is a chain wheel 18C
It consists of an outer wheel 106 arranged rotatably inside and a stationary inner wheel 107 which meshes with this outer wheel. The annular gear pump is followed by a lateral closing part 108, which is non-rotatably connected with the cam bearing by means of a pin 109. The inner wheel 107 is screwed to the closing part 108 by screws (not shown), so that it cannot rotate. The outer wheel 106-as shown in FIG. 6-is supported eccentrically with respect to the inner wheel 107 in an enlarged portion 110 on the end side of the chain wheel 18C. The connecting member 12A is designed to be loaded in a single-acting manner, corresponding to the structure according to FIG. The supply of the pressure medium takes place from the low-pressure side in the same way as in the embodiment according to FIG. 4, but, unlike the embodiment according to FIG. 4, the passage 111 in the chain wheel 18C is adapted to the pump configuration. ing. I will not go into all the details here. This is because it is clearly shown in the drawing and is easy to understand. The high-pressure outlet side 112 is also located in the chain wheel 18C and further has a slit 113 extending in the longitudinal direction, which slit is located in the pressure chamber 114 of the connecting member and through the connecting passage in the central member. It leads to. The function of a G-rotor pump or also an annular gear pump is well known and the function of the overall device is not different from the embodiment according to FIGS. 2 and 4 and therefore will not be described here.

─────────────────────────────────────────────────── ─── Continuation of the front page (56) References Japanese Unexamined Patent Publication No. 3-112604 (JP, A) Actual Development No. 5-1802 (JP, U) Special Table No. 5-500403 (JP, A) International Publication 91/003628 (WO, A1) (58) Fields investigated (Int.Cl. ⁷ , DB name) F01L 1/34

Claims (9)

(57) [Claims] 1. A camshaft (10) for an internal combustion engine, a pump (26)
A hydraulic force control device that is rotated by a connecting member (12) that is movable in the longitudinal direction by the pressure generated by the connecting member, the connecting member having a cam shaft and Chain drive driven by an internal combustion engine (1
8) relative rotation with the connecting member, the connecting member is axially movable by the liquid pressure controlled by the magnet valve, and the chain wheel (18) houses the central member (11), The central member is non-rotatably connected to the camshaft (10), and the pressure-loaded connecting member (12) is located between the central member and the cylindrical extension (17) of the chain wheel. , Central members (11)
At least one between the pump and the connecting member and chain wheel
Passages (39-41) are formed for connection to two pressure chambers (43), and the pressure chambers are connected to the valve body (46) of the solenoid valve. It is formed as a pump (26), and the chain wheel (18) has an eccentric hole (25) inside the end facing the camshaft (10), and this eccentric hole has a radial piston pump (26). ), The radial piston pump is a stator (2
7), the stator accommodating at least one transfer piston (30), the outer crest of which lies on a non-rotating ring (31) located in the eccentric hole. A hydraulic controller characterized in that it slides along the passage (39-41) and the connecting portion extends from the radial piston pump. 2. The connecting member (12) is loaded from one side, and the pressing spring (22) arranged inside the hollow of the connecting member acts on the connecting member in the direction opposite to the liquid pressure. The described device. 3. The connecting member (12A) is loaded in a double-acting manner, the valve body (74) of the solenoid valve has two valve conical portions (75, 76), and each valve conical portion is a connecting member. 2. Device according to claim 1, characterized in that it controls each one pressure chamber (63, 64). 4. Apparatus according to claim 1, wherein the stator (27) is non-rotatably connected to the camshaft bearing (20) via a connecting pin (28). 5. A low pressure side of a radial piston pump (56.8)
2. The device according to claim 1, wherein the pressure medium supply in 0) is connected to the pressure oil circuit of the engine. 6. The device according to claim 3, wherein the radial piston pump has two discharge outlets (84, 85), each discharge outlet being connected to a respective one of the pressure chambers of the connecting member. 7. The device according to claim 3, wherein at least a part of each of the central member (11B), the connecting member (12A), the chain wheel (18B) and the radial piston pump is located in one radial plane. 8. The ring (95) is an extension (9) of the chain wheel (18B).
Device according to claim 7, which is eccentrically supported by 7). 9. The valve body has a plunger, which is firmly connected to the armature (50) of the solenoid valve,
2. The device according to claim 1, which extends coaxially with the central member, the valve body being arranged in an enlarged hole (44) in the central member and controlling the passage connected to the pressure chamber of the connecting member.