JP4105201B2 - Valve timing adjustment device - Google Patents

Description

  The present invention relates to a valve timing adjusting device that changes the opening / closing timing of an intake / exhaust system valve in accordance with engine operating conditions.

  FIG. 11 is a cross-sectional view showing a conventional valve timing adjusting device disclosed in Patent Document 1, for example. In the figure, 1 is a camshaft for opening and closing a valve of an engine system, 2 is a housing rotatably mounted on the camshaft 1, and 2 a is projected on the inner peripheral surface of the housing 2 at a predetermined interval. The housing 2 is configured to receive a rotational driving force from an engine crankshaft (not shown). Reference numeral 3 denotes a rotor connected and fixed to the camshaft 1 and housed in the housing 2. Reference numeral 3 a denotes a plurality of pieces extending in a radial direction from the outer peripheral surface of the rotor 3 and slidingly contacting the inner peripheral surface of the housing 2 between the shoes 2 a. The housing 2 and the rotor 3 are rotatable relative to each other.

  4 is a pin hole penetrating the shoe 2 a in the radial direction of the housing 2, 5 is a lock pin slidably inserted into the pin hole 4, and 6 is inserted into the pin hole 4 so that the lock pin 5 is inserted into the housing 2. A radially energizing spring, 6a is a blind plug that closes the pin hole 4 on the outer diameter side of the housing 2 and presses the spring 6, and 7 is a lock hole that is provided in the rotor 3 to removably fit the lock 5 The lock hole 7 can be connected to the pin hole 4. The lock hole 7 is supplied with hydraulic pressure in a direction against the urging force of the spring 6 from a hydraulic control system.

Next, the operation will be described.
In a state where the lock pin 5 on the housing 2 side is fitted into the lock hole 7 of the rotor 3 by the biasing force of the spring 6 and the housing 2 and the rotor 3 are locked so as to be able to rotate synchronously, the hydraulic pressure supplied to the lock hole 7 is increased. When the pressure becomes higher than a predetermined value, the lock pin 5 retracts from the lock hole 7 against the urging force of the spring 6 by the hydraulic pressure, so that the housing 2 and the rotor 3 are unlocked to rotate relative to each other. The opening / closing timing of the valve is adjusted by the relative rotation.

JP-A-1-92504 (Specification, page 3, line 18 to page 7, line 3, FIG. 2)

  Since the conventional valve timing adjusting device is configured as described above, a blind plug 6a for closing the pin hole 4 on the outer diameter side of the housing 2 and pressing the spring 6 is indispensable. There is a problem that measures to prevent oil spillage and measures to prevent the valve timing adjusting device from coming out of the pin hole 4 due to the rotational centrifugal force are required. For example, when the blind plug 6a is mounted, after inserting a sealing material for airtightness into the pin hole 4, the blind plug 6a is screwed to the pin hole 4 and further, for the purpose of preventing the screw from being removed. There was a problem that agent coating, caulking, etc. were required. When the lock pin 5 and the spring 6 are assembled to the shoe 2a of the housing 2, the lock pin 5 and the spring 6 are inserted into the lock hole 7 from the radial direction of the housing 2, and the blind plug 6a is attached. Furthermore, in order to prevent the blind plug 6a from being removed, for example, application of an adhesive or caulking work is required as described above, and the assembly work of the lock parts from the radial direction is troublesome. There is a problem that the productivity of the valve timing adjusting device is lowered due to poor attachment. As another conventional valve timing adjusting device, all locking parts such as a locking member and a biasing member that biases the locking member in the locking direction of the housing and the rotor are assembled in the axial direction with respect to the shoe of the housing. In some cases, there is a possibility, but in this case, the rotor is easily inclined by the elastic force of the urging member at the time of assembling the lock part, and therefore there is a problem that the assemblability of the valve timing adjusting device is very poor.

  The present invention has been made to solve the above-described problems, and can easily and accurately assemble a lock component that locks the first and second rotating bodies on the same axis so that they can rotate synchronously. It is an object of the present invention to provide a valve timing adjusting device that can improve its assemblability and can be molded at a low cost, such as forging, casting, and sintering.

A valve timing adjusting device according to the present invention includes a first rotating body that includes a case that is rotatably provided on a camshaft that is driven in synchronization with the rotation of an engine, and that has a plurality of shoes projecting from an inner peripheral surface thereof; A second rotating body, which is connected and fixed to the camshaft, is in sliding contact with the inner surface of the first rotating body, and has a lock groove provided in the axial direction on the outer peripheral surface of the boss portion, and a tip portion engages with the lock groove. A plate-like lock member that locks the first rotary body and the second rotary body so as to be able to rotate synchronously, and retracts from the lock groove to release the lock, and the plate-like lock member is arranged in the direction of the lock groove. And at least one of the shoes along the axial direction, at least one end in the axial direction is open to the axial end surface of the shoe, and the slidable contact surface side with the second rotating body is Open the plate lock member And a engaging groove which housed bearing, is provided with a drain groove communicating with the engaging groove in the axial end surface of the case.

As described above, according to the present invention, at least one of the plurality of shoes on the inner peripheral surface of the case included in the first rotating body rotatably provided on the camshaft that is driven in synchronization with the rotation of the engine. The shoe is provided with an engagement groove having at least one axial end opening on the axial end surface of the shoe and an opening on the sliding contact surface side of the second rotation body that can rotate relative to the first rotation body. Since the plate-like lock member is stored and supported, the plate-like lock member can be easily assembled simply by slidingly inserting the plate-like lock member into the engagement groove from the axial end surface of the case along the axial direction. As a result, the assembling property can be improved, and the number of parts can be reduced because no lock-off prevention parts are required. In addition, since the drain groove communicated with the engagement groove is provided on the end surface in the axial direction of the case, the lock parts for locking the first and second rotating bodies on the same axis so as to be able to rotate synchronously are easily and highly accurate. Can be assembled to. As a result, simple axial stacking can be performed, the assembling property is improved and the productivity is excellent, and there is an effect that mold forming such as forging, casting and sintering is possible and can be produced at low cost.

An embodiment of the present invention will be described below.
Embodiment 1 FIG.
1 is a longitudinal side view showing a valve timing adjusting apparatus according to Embodiment 1 of the present invention, FIG. 2 is a longitudinal front view of FIG. 1, and FIG. 3 is an exploded perspective view of the main part of FIGS. In the figure, reference numeral 21 denotes a first rotating body rotatably provided on a camshaft (not shown) for opening and closing an engine valve, and this first rotating body 21 is driven by a rotational driving force from a crankshaft of the engine. Is provided with a timing pulley 22 and a case 23 having a cylindrical section passing through and fixed to one side surface of the timing pulley 22, and a plurality of shoes 23 a are provided on the inner peripheral surface of the case 23. Projected in the circumferential direction at a predetermined interval.

  Reference numeral 24 denotes a rotor housed in the case 23 and connected and fixed to the camshaft. The rotor 24 is a second rotating body that can rotate relative to the first rotating body 21. A plurality of vanes 24a extending in the radial direction are projected on the rotating body portion, and the tips of these vanes 24a are connected to the inner peripheral surface of the case 23 via a chip seal (seal member) 48, which will be described later, between the shoes 23a. Is in sliding contact. Note that the tip of each shoe 23a is in sliding contact with the rotating body of the rotor 24 via chip seals (seal members) 43, 44, and 46, which will be described later. Reference numeral 25 denotes an advance hydraulic chamber for rotating each vane 24a in the advance direction, and 26 denotes a retard hydraulic chamber for rotating each vane 24a in the retard direction. The hydraulic chamber 26 is formed in a fan column shape between each shoe 23 a and each vane 24 a between the case 23 and the rotor 24.

  27 is a first plate assembled on the axial end surface of the case 23 opposite to the timing pulley 22, 28 is a second plate assembled on the surface of the first plate 27, and 29 is a second plate 28. The cover member 30 attached to the surface is a spring interposed between the second plate 28 and the cover member 29. The first plate 27, the second plate 28, and the cover member 29 are the first plate 27 and the cover member 29. The unit cover 31 is configured by bending and crimping the peripheral edge of the plate 27 in the direction of the rotation center. Reference numeral 32 denotes a bolt that fastens the timing pulley 22, the case 23, and the first plate 27 and the second plate 28 of the unit cover 31 together.

  Reference numeral 33 denotes a lock part storage cavity provided in one shoe 23a. The cavity 33 extends in the entire axial length of the shoe 23a and opens at both axial end faces of the shoe 23a. Reference numeral 34 denotes an engagement groove for engaging a lock member that is provided on the shoe 23a and opens to the tip (sliding contact surface with the rotor 24) side of the shoe 23a. The engagement groove 34 extends in the axial direction of the shoe 23 a and communicates with the cavity portion 33 with its entire axial length, and both ends of the engagement groove 34 in the axial direction are the same as in the case of the cavity portion 33. Opening is made at both axial end faces of 23a. Accordingly, the engagement groove 34 is a through groove that penetrates one shoe 23a in the axial direction. A drain hole 35 opens to the outer surface of the case 23 and communicates with the cavity 33. That is, the drain hole 35 is formed on the end surface of the case 23 in the axial direction.

  Reference numerals 36 and 37 denote circumferential oil passages provided on both end surfaces in the axial direction of the shoe 23a having the engagement groove 34. One of the circumferential oil passages 36 is formed on one end surface in the axial direction of the shoe 23a. A space surrounded by an L-shaped notch 36a, a side wall surface of the timing pulley 22 that covers the notch 36a with one end surface in the axial direction of the shoe 23a, and a rotor 24 that is in sliding contact with the tip end surface of the shoe 23a. And extending in the circumferential direction along the slidable contact surface of the rotor 24. The other circumferential oil passage 37 includes a cutout portion 37a having an L-shaped cross section formed on the other axial end surface of the shoe 23a, and a first plate that covers the cutout portion 37a with the other axial end surface of the shoe 23a. 27 and a rotor 24 that is in sliding contact with the tip end surface of the shoe 23 a, and extends in the circumferential direction along the sliding contact surface of the rotor 24. The circumferential oil passages 36 and 37 are divided by the engagement groove 34.

  38 and 39 are seal grooves provided at two positions on both sides of the plate-like lock member 41 provided on the sliding contact surface portion of the shoe 23a having the engagement groove 34 with the rotor 24, and these seal grooves 38 and 39 are It extends in the axial direction and communicates with the circumferential oil passages 36 and 37.

  Reference numeral 40 denotes a lock groove provided on the outer peripheral surface of the rotating body of the rotor 24, and the lock groove 40 extends in the axial direction of the rotor 24. Reference numeral 41 denotes a plate-like lock member fitted and engaged with the engagement groove 34 so as to be slidable in the radial direction of the case 23. The plate-like lock member 41 is removably fitted into the lock groove 40. Then, the case 23 (first rotating body 21) and the rotor (second rotating body) 24 are locked so as to be able to rotate synchronously, and the case 23 and the rotor 24 are unlocked by retracting from the lock groove 40. To enable relative rotation. Here, each of the case 23 and the plate-like lock member 41 is made of a material having substantially the same linear expansion coefficient. For example, the case 23 and the plate-like lock member 41 are made of an iron-based sintered metal material or the same kind of material. To do.

  As shown in FIGS. 1 and 3, the plate-like lock member 41 is formed of a substantially U-shaped plate-like member having a recessed portion 41a and extends in the axial direction of the shoe 23a. 41b is an engagement portion of the plate-like lock member 41 with respect to the engagement groove 34, and 41c and 41d are oil-receiving pressure receiving surface portions provided at both ends in the longitudinal direction of the engagement portion 41b, and these pressure receiving surface portions 41c, 41c, 41d is formed by cutting away the corners at both ends in the longitudinal direction of the engaging portion 41b in the plate-like lock member 41, and the two seal grooves 38, 39 and the circumferential direction via the pressure receiving surface portions 41c, 41d. The oil passages 36 and 37 communicate with each other in series. Reference numeral 42 denotes a spring which is housed in the cavity 33 and serves as a biasing means for biasing the plate-like lock member 41 toward the rotation center of the case 23.

  Reference numerals 43 and 44 denote chip seals (seal members) fitted and held in the seal grooves 38 and 39, respectively. These chip seals 43 and 44 have bending elastic piece portions 43a and 44a, respectively. The tip seals 43 and 44 are pressed against the rotating body of the rotor 24 by the resilient force of the portions 43a and 44a. Here, the seal grooves 38 and 39 are formed so that each groove width is wider than the thickness of the chip seals 43 and 44, and the chip seals 43 and 44 are arranged in the circumferential direction of the shoe 23a in the seal grooves 38 and 39. It is fitted and held movably.

  45 is a seal groove provided on the tip surface of another shoe 23 a that does not have the plate-like lock member 41, 46 is a chip seal (seal member) fitted and held in the seal groove 45, and 47 is the rotor 24. Seal grooves 48 provided on the front end surfaces of the vanes 24a are chip seals (seal members) fitted and held in the seal grooves 47. The seal grooves 45 and 47 and the chip seals 46 and 48 are formed of the shoe 23a and The vane 24a extends along the entire length in the axial direction, and both axial ends of the seal grooves 45 and 47 are opened at both axial ends of the shoe 23a and the vane 24a.

  Here, the cavity 33 of the case 23, the engaging groove 34, the plate-like lock member 41, the chip seals (seal members) 43, 44, 46, and the chip seal 48 of the rotor 24 have their axial lengths in the case 23. And the length of the rotor 24 in the axial direction is substantially equal.

  4 is a schematic configuration diagram showing a hydraulic control system of a lock member and a seal member of the valve timing adjusting apparatus according to Embodiment 1 of the present invention. The same reference numerals are given to the same or corresponding parts as in FIGS. explain. In the figure, 51 is an oil pump, 52 is an oil control valve (hereinafter referred to as OCV), 53 is a first hydraulic passage, and 54 is a second hydraulic passage. It also serves as a hydraulic pressure supply means for applying an oil pressure in a direction against the urging force.

  The first hydraulic passage 53 communicates with one seal groove 38, and the seal groove having a groove width wider than the thickness of the tip seal 43 due to the hydraulic pressure supplied from the first hydraulic passage 53 to the seal groove 38. The chip seal 43 in the seal groove 38 is pushed in the groove width direction of 38. The second hydraulic passage 54 communicates with the other seal groove 39, and oil pressure is supplied from the second hydraulic passage 54 into the seal groove 39, so that the other tip seal 44 is moved by the oil pressure. The seal groove 39 is pushed in the groove width direction. When the oil pressure applied to the plate-like lock member 41 becomes higher than a predetermined value, the plate-like lock member 41 resists the urging force of the spring 42 with the oil pressure (unlocking the lock groove 40). When the oil pressure becomes a predetermined value or less, the urging force of the spring 42 moves toward the rotation center of the rotor 24. One of the first hydraulic passage 53 and the second hydraulic passage 54 communicates with the advance hydraulic chamber 25 and the other communicates with the retard hydraulic chamber 26.

  Next, assembly of the valve timing adjusting device according to the first embodiment will be described. First, in a state where the rotor 24 is housed in the case 23, chip seals (seal members) 43, 44, 46, 48 are slid into the seal grooves 38, 39, 45, 47 from the respective axial opening ends. Next, the plate-like lock member 41 is slid and inserted into the engagement groove 34 from the axially open end of the engagement groove 34. At the initial insertion stage, the spring 42 is set in the recess 41a of the plate-like lock member 41. Then, by pressing the plate-like lock member 41 in the axial direction along the engagement groove 34 while compressing the spring 42, the spring 34 is accommodated in the cavity 33, and the plate-like lock member 41 is engaged with the engagement groove. 34 is assembled in a state of being fitted over the entire length in the axial direction. In this manner, the case 23, the rotor 24, the plate-like lock member 41, the spring 42, and the chip seals 43, 44, 46, 48 are assembled in a unit state. After the assembly, the timing pulley 22, the case 23, and the first plate 27 and the plate 28 are fastened together with the bolt 32, and the assembly of the valve timing adjusting device is completed.

Next, the operation will be described.
In a state where the plate-like lock member 41 is fitted into the lock groove 40 by the urging force of the spring 42 and locks the first rotary body 21 and the rotor (second rotary body) 24, the first rotary body 21 and the rotor 24. Is held in a state that allows synchronous rotation. In this state, when oil pressure is supplied from the first hydraulic passage 53 to the one seal groove 38 via the OCV 52 from the oil pump 51 in FIG. 4, the oil pressure causes the tip seal 43 to pass through the seal groove 38. The shoe 23 a is moved in one direction along the circumferential direction of the shoe 23 a and passes through the one tip seal 43 and passes through the circumferential oil passages 36 and 37, and the other tip seal 44 is moved to the one tip seal 43. It is moved in the same direction as the moving direction and pressed against the inner wall surface of the other seal groove 39. Here, the hydraulic pressure supplied from one seal groove 38 to the circumferential oil passages 36 and 37 acts on the other chip seal 44 through the pressure receiving surface portions 41c and 41d of the plate-like lock member 41. In this state, Both tip seals 43, 44 are strong against the peripheral surface of the rotating body of the rotor 24 by the elastic force of the bending elastic pieces 43 a, 44 a and the back pressure (hydraulic pressure) acting on each tip seal 43, 44. Since they are in sliding contact, oil leakage from between the sliding contact surfaces of the shoe 23a and the rotating body portion of the rotor 24 can be reliably prevented.

  When the oil pressure acting on the pressure receiving surface portions 41c and 41d of the plate-like lock member 41 in the circumferential oil passages 36 and 37 becomes higher than a predetermined value, the plate-like lock member 41 resists the spring 42 by the oil pressure. When the plate-like lock member 41 is retracted from the lock groove 40 of the rotor 24, the first rotary body 21 and the rotor (second rotary body) 24 are unlocked and are relatively The opening and closing timing of the intake / exhaust system valve of the engine is controlled by the relative rotation.

  In the unlocked state as described above, when the hydraulic pressure acting on the pressure receiving surface portions 41 c and 41 d of the plate-like lock member 41 is reduced to a predetermined value or less, the plate-like lock member 41 is forced by the urging force of the spring 42. When the lock groove 40 reaches the position facing the plate-shaped lock member 41 by moving in the direction of the rotation center and slidably contacting the circumferential surface of the rotary drum portion of the rotor 24, the plate-shaped lock member 41 enters the lock groove 40. The first rotating body 21 and the rotor 24 are locked so that they can rotate synchronously.

  The above is the case where the hydraulic pressure from the OCV 52 is supplied to the circumferential oil passages 36 and 37 from the one seal groove 38 through the first hydraulic passage 53, and the OCV 52 is in the state shown in FIG. 4 according to the operating conditions of the engine. , The hydraulic pressure from the OCV 52 passes through the second hydraulic passage 54 and is supplied from the other seal groove 39 to the circumferential oil passages 36 and 37. In this case as well, the first rotor 21 and the rotor 24 Locking and unlocking operations are performed similarly.

  According to the first embodiment described above, each of the cavity portion 33, the engagement groove 34, and the seal grooves 38, 39, and 45 of the case 23 extends in the axial direction of the shoe 23a and is formed on both end surfaces of the shoe 23a in the axial direction. Each axial end surface of each of the hollow portion 33, the engagement groove 34, and each of the seal grooves 38, 39, 45 is opened, and even in each seal groove 47 of the rotor 24, both axial ends are shafts of the vane 24a. Since the opening is made at both end surfaces in the direction, the plate-shaped lock member 41 is slid and inserted into the engagement groove 34 from the axial opening end of the engagement groove 34 in a state where the rotor 24 is housed in the case 23. In the insertion process, the spring 42 is fitted and set in the recessed portion 41 a of the plate-like lock member 41, and in this state, the plate-like lock member 41 is simply pushed along the engagement groove 34, and the spring 42 is inserted into the cavity portion 33. It is paid, and a plate-like locking member 41 over the entire axial length of the engaging groove 34 can be assembled in a state of being fitted held, it is possible to perform the assembling work easy. Further, even in the seal grooves 38, 39, 45, 47, since both ends in the axial direction are open at both end faces in the axial direction of the shoe 23a and the vane 24a, the seal grooves 38, 39, 45, 47 are provided. The chip seals 43, 44, 46, and 48 can be easily assembled by simply inserting the chip seals 43, 44, 46, and 48 from the respective axially open ends. In particular, the plate-like lock member 41 made of a plate-like member has improved axial assembly along the engagement groove 34, and one side inner wall surface of the recessed portion 41 a when sliding into the engagement groove 34. Thus, the spring 42 can be hooked and inserted into the cavity 33. Therefore, according to the first embodiment, there is an effect that the parts assembling property is improved and the production cost can be reduced.

  Further, according to the first embodiment, as described above, the cavity 33 for storing the lock part penetrates the case 23 in the axial direction, and is in the engagement groove 34 and the seal grooves 38, 39, 45. However, since both ends in the axial direction are open at both end surfaces in the axial direction of the shoe 23a and the circumferential oil passages 36 and 37 are formed in a substantially L shape in cross section, the case 23 is forged, cast and sintered. Thus, it is possible to mold the product, and the mass productivity can be improved and the production cost can be reduced.

  Further, according to the first embodiment, the tip seals 43 and 44 are disposed on the sliding contact surface with the rotor 24 in the shoe 23a having the plate-like lock member 41 at two positions on both sides of the plate-like lock member 41. Therefore, the locking action and locking of the plate-like lock member 41 are performed regardless of whether the hydraulic pressure is supplied to either the advance hydraulic chamber 25 or the retard hydraulic chamber 26 formed on both sides in the circumferential direction of the shoe 23a. The short-circuit between the advance hydraulic chamber 25 and the retard hydraulic chamber 26 can be prevented by the two tip seals 43 and 44 without impairing the releasing operation, and therefore there is an effect that oil leakage can be prevented. .

  Furthermore, according to the first embodiment, the plate-like lock member 41 and the case 23 that holds the plate-like lock member 41 so as to be slidable are made of a material having substantially the same linear expansion coefficient. There is an effect that the optimum sliding function of the plate-like lock member 41 is maintained regardless of the change in the environmental temperature.

  Further, according to the first embodiment, the seal grooves 38 and 39 into which the two chip seals 43 and 44 are inserted are formed so that the respective groove widths are wider than the thickness of the chip seals 43 and 44. Since the tip seals 43 and 44 can move in the circumferential direction of the shoe 23a in the seal grooves 38 and 39, the hydraulic pressure is applied to either the advance hydraulic chamber 25 or the retard hydraulic chamber 26. When supplied, both tip seals 43, 44 move to the lower oil pressure in the respective seal grooves 38, 39, so that either one of the two tip seals 43, 44 is on the high pressure side. The other side becomes the low pressure side, and the sealing function of the high pressure side tip seal 43 or 44 is lowered, but the sealing function of the low pressure side tip seal 44 or 43 is increased, and therefore the tip seals thereof are increased. There is an effect that it constitutes a kind of directional control valve by 3,44.

  Further, according to the first embodiment, notched pressure receiving surface portions 41c and 41d are formed at both longitudinal ends of the engaging portion 41b of the plate-like lock member 41 with respect to the engaging groove 34, and the pressure receiving surface portions 41c and 41d are formed. Since the circumferential oil passages 36 and 37 that communicate with each other between the two seal grooves 38 and 39 are provided at both axial end surfaces of the shoe 23a to which the plate-like lock member 41 is assembled, the plate-like lock member 41, the hydraulic pressure acting on both side surfaces of the plate-like lock member 41 can be equalized, so that there is no pressure difference between both sides of the plate-like lock member 41. It is possible to prevent the occurrence of tilt, twist, deformation, and the like, and there is an effect that the locking operation and the unlocking operation of the plate-like lock member 41 can be performed smoothly at all times.

Embodiment 2. FIG.
FIG. 5 is a perspective view showing a plate-like lock member of the valve timing adjusting apparatus according to Embodiment 2 of the present invention. In the figure, reference numerals 41e and 41f denote two protrusions for oil passage formation provided between the pressure receiving surface portions 41c and 41d at both ends in the longitudinal direction of the engaging portion 41b of the plate-like lock member 41. 41f is made to slidably contact the circumferential surface of the rotating body of the rotor 24 in FIGS. 1 to 3 or contact the groove bottom surface of the lock groove 40. That is, in the second embodiment, the protrusions 41e and 41f are in sliding contact with the circumferential surface of the rotating body of the rotor 24 by the biasing force of the spring 42 in FIGS. In the abutted state, an oil passage that communicates the two seal grooves 38 and 39 via the circumferential oil passages 36 and 37 is formed between the protrusions 41e and 41f, and the engagement of the plate-like lock member 41 is established. The surface between the projecting portions 41e and 41f in the joint portion 41b is configured to be a pressure receiving surface portion.

  According to the second embodiment, the surface between the protrusions 41e and 41f in the engagement part 41b is formed by the two protrusions 41e and 41f provided in the engagement part 41b of the plate-like lock member 41. The joint portion 41b can be formed as a pressure receiving surface portion at the center in the longitudinal direction, and the pressure receiving surface portions and pressure receiving surface portions 41c and 41d at both ends in the longitudinal direction of the engagement portion 41b act in a balanced manner on the entire area of the engagement portion 41b. For this reason, problems such as tilting and twisting of the plate-like lock member 41 can be more reliably prevented, and the operation performance when the plate-like lock member 41 is locked and unlocked is further improved. There is an effect that can be.

Embodiment 3 FIG.
6 is a perspective view showing a plate-like lock member of a valve timing adjusting apparatus according to Embodiment 3 of the present invention. In the figure, reference numerals 41g and 41h denote groove-like pressure receiving surface portions that are provided between the pressure receiving surface portions 41c and 41d at both ends in the longitudinal direction in the engaging portion 41b of the plate-like lock member 41. That is, in the third embodiment, groove-shaped pressure receiving surface portions 41g and 41h are formed in place of the projection portions 41e and 41f of the plate-like lock member 41 according to the second embodiment. Therefore, in the case of the third embodiment, the same effect as in the second embodiment can be obtained.

Embodiment 4 FIG.
7 is an exploded perspective view of a main part of a valve timing adjusting device according to Embodiment 4 of the present invention. FIG. 8 is a cross-sectional view of the valve timing adjusting device of FIG. The same or corresponding parts are denoted by the same reference numerals, and redundant description is omitted. In FIG. 7, reference numeral 41-1 denotes a plate-like first lock member that is fitted and held in the engagement groove 34 of the case 23 and extends in the axial direction. The first lock member 41-1 has a seat plate 41A at the base end. It has one. Reference numeral 41-1a denotes a tip engagement portion (hereinafter simply referred to as an engagement portion) of the first lock member 41-1 with respect to the lock groove 40 of the rotor 24. The engagement portion 41-1a is formed in a V-shaped cross section. ing. 42-1 is a spring as an urging means for urging the first lock member 41-1 in the direction of the rotation center of the case 23 via the seat plate 41A, and 42A has a spring receiving hole h and is connected to the seat plate 41A. This is a spring receiving member that holds the spring 42-1 between them.

  Reference numeral 41-2 denotes a second lock member paired with the first lock member 41-1, and the second lock member 41-2 has an engagement portion 41-2a with the lock groove 40 formed in a U-shaped cross section. The seat plate 41B is integrally provided at the base end. 42-2 is a spring (biasing means) for urging the second lock member 41-2, 42B is a spring receiving member having a spring receiving hole h, 411 is the first lock member 41-1 system and the second lock member 41. -2 is a partition plate interposed between the two systems.

  In the fourth embodiment, the plate-like lock member 41 according to the first to third embodiments described above is configured by a combination of the first lock member 41-1 and the second lock member 41-2. The engagement portion 41-1a of the first lock member 41-1 is formed in a V-shaped cross section, and the engagement portion 41-2a of the second lock member 41-2 is formed in a U-shaped cross section.

  In assembling the first lock member 41-1 and the second lock member 41-2 according to the fourth embodiment, the first lock member 41-1 and the spring 42-1 and spring receiving member 42A of this system are combined. Similarly, the second lock member 41-2, the spring 42-2, and the spring receiving member 42B are unitized. Then, the first lock member 41-1 and the second lock member 41-2 are sequentially slid and inserted into the engagement groove 34 of the case 23. In the insertion process, the seat plate 41A and the spring support of the first lock member 41-1 system. A partition plate 411 is interposed between the member 42A and the seat plate 41B and the spring receiving member 42B of the second lock member 41-2 system. In this state, the first lock member 41-1 and the second lock member 41-2 are sequentially pushed along the engagement groove 34 so that the first lock member 41-1 and the second lock member 41-2 are engaged with each other. 34 is slidably held in the radial direction of the case 23 at an adjacent position along the axial direction, and the seat plates 41A and 41B, the springs 42-1 and 42-2, and the spring receiving members 42A and 42B are formed in the cavity 33. As a result, the assembly of the first lock member 41-1 system and the second lock member 41-2 system to the case 23 is completed.

Next, the operation will be described.
FIG. 9 is an explanatory view of the locking operation of the valve timing adjusting apparatus according to Embodiment 4 of the present invention. At the time of relative rotation between the case (first rotating body) 23 and the rotor (second rotating body) 24, the oil pressure acting on the first lock member 41-1 and the second lock member 41-2 is a predetermined value or less. The first locking member 41-1 and the second locking member 41-2 are moved toward the rotation center of the rotor 24 by the urging force of the springs 42-1 and 42-2 of the respective systems. When the engagement portions 41-1a and 41-2a of the first lock member 41-1 and the second lock member 41-2 are fitted into the lock groove 40, the case 23 and the rotor 24 are relatively rotated. Securely restrained. However, the relative positions of the case 23 and the rotor 24 (first and second lock members 41-1 when the first and second lock members 41-1 and 41-2 are operated by the urging force of the springs 42-1 and 42-2. , 41-2 and the relative position of the lock groove 40) may be displaced as shown in FIG. In this case, since the engagement portion 41-1a of the first lock member 41-1 has a V-shaped cross section, the one-side inclined surface of the V-shaped surface is slidably guided to one inner wall surface of the lock groove 40. The As a result, the displacement of the relative position between the case 23 and the rotor 24 is corrected by the first lock member 41-1, and when the case 23 and the rotor 24 become the normal relative position, the second lock member 41-2 is corrected. Is fitted and aligned in the lock groove 40 (see FIG. 9D), and the case 23 and the rotor 24 are securely locked.

  According to the fourth embodiment described above, the engagement portion 41-1a of the first lock member 41-1 with respect to the lock groove 40 is formed in a V-shaped cross section, and the second lock member 41-2 is engaged. By forming the portion 41-2a to have a U-shaped cross section, even when a slight misalignment occurs between the relative positions of the case 23 and the rotor 24 when the relative rotation of the case 23 and the rotor 24 is restricted, the misalignment of the first lock member 41- The first locking portion 41-1a can be corrected, and after the correction, the second lock member 41-2 is fitted and aligned in the lock groove 40, so that the case 23 and the rotor 24 can be securely locked. There is an effect that the performance can be improved.

Embodiment 5. FIG.
10 is an exploded perspective view of a lock mechanism according to Embodiment 5 of the present invention. The same or corresponding parts as those in FIG. In the fifth embodiment, the fitting head 42C for the cavity 33 of the case 23 is formed integrally with the spring receiving members 42A and 42B according to the fourth embodiment, and the fitting head 42C is formed on the cavity 33. The other configurations of the first and second lock members 41-1 and 41-2 are the same as those of the fourth embodiment.

  According to the fifth embodiment, the head portions 42C of the spring receiving members 42A and 42B are aligned with the inner wall surface of the cavity portion 33 when the first and second lock members 41-1 and 41-2 are attached to the case 23. By doing so, there is an effect that the assembling property of the lock parts such as the first and second lock members 41-1 and 41-2 and the springs 42-1 and 42-2 and the spring receiving members 42A and 42B is improved.

It is a vertical side view which shows the valve timing adjustment apparatus by Embodiment 1 of this invention. It is a vertical front view of FIG. It is the perspective view which decomposed | disassembled the principal part of FIG. 1 and FIG. It is a schematic block diagram which shows the hydraulic control system of the lock member of the valve timing adjustment apparatus by Embodiment 1 of this invention, and a seal member. It is a perspective view which shows the plate-shaped locking member of the valve timing adjustment apparatus by Embodiment 2 of this invention. It is a perspective view which shows the plate-shaped locking member of the valve timing adjustment apparatus by Embodiment 3 of this invention. It is the perspective view which decomposed | disassembled the principal part of the valve timing adjustment apparatus by Embodiment 4 of this invention. It is sectional drawing in the assembly state of the valve timing adjustment apparatus of FIG. It is locking operation explanatory drawing of the valve timing adjustment apparatus by Embodiment 4 of this invention. It is a disassembled perspective view of the locking mechanism by Embodiment 5 of this invention. It is sectional drawing which shows the conventional valve timing adjustment apparatus.

Explanation of symbols

  21 1st rotator, 23 case, 23a shoe, 24 rotor (2nd rotator), 34 engagement groove, 36, 37 circumferential oil passage (oil passage), 38, 39 seal groove, 40 lock groove, 41 plate Shaped locking member, 41-1 first locking member, 41-2 second locking member, 41b, 41-1a, 41-2a engagement site, 41c, 41d pressure receiving surface, 42, 42-1 and 42-2 spring ( Urging means), 43, 44 Tip seal (seal member), 51 Oil pump (hydraulic supply means).

Claims (2)

A first rotating body provided with a case rotatably provided on a camshaft that is driven in synchronism with the rotation of the engine, and having a plurality of shoes projecting from an inner peripheral surface thereof; A second rotating body having a locking groove which is in sliding contact with the inner surface of the first rotating body and is provided in the axial direction on the outer peripheral surface of the boss portion; A plate-like lock member that locks the body so as to rotate synchronously, and retreats from the lock groove to release the lock; and a biasing means that biases the plate-like lock member in the direction of the lock groove; At least one of the shoes is provided along the axial direction, and at least one axial end opens to the axial end surface of the shoe and the sliding contact surface side with the second rotating body opens to store the plate-like lock member An engaging groove for supporting the shaft of the case Providing the drain groove communicating with said engaging groove in direction end face valve timing control apparatus according to claim. A first rotating body provided with a case rotatably provided on a camshaft that is driven in synchronism with the rotation of the engine, and having a plurality of shoes projecting from an inner peripheral surface thereof; A second rotating body having a locking groove which is in sliding contact with the inner surface of the first rotating body and is provided in the axial direction on the outer peripheral surface of the boss portion; A plate-like lock member that locks the body in a synchronously rotatable manner and retreats from the lock groove to release the lock; and a biasing means that biases the plate-like lock member in the direction of the lock groove; A hydraulic pressure supply means for applying a hydraulic pressure in a direction against the urging means to the plate-like lock member; and at least one of the shoes provided along the axial direction, at least one axial end at an axial end surface of the shoe. Open and sliding contact with the second rotating body And a engaging groove side stores bearing the opening to the plate-like lock member, the valve timing control apparatus characterized in that a drain groove communicating with the engaging groove in the axial end surface of the case.

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