JP4690986B2 - Mounting structure of vane type hydraulic actuator for variable stroke characteristics engine - Google Patents

Description

  In the present invention, a piston and a crankshaft are connected to a control shaft via a variable stroke link mechanism, and a vane type hydraulic actuator is provided on the control shaft, and the control shaft is driven by the hydraulic actuator to provide a variable stroke link mechanism. The present invention relates to a vane type hydraulic actuator mounting structure in a variable stroke characteristic engine that operates to vary a moving stroke of a piston.

Conventionally, an upper link having one end connected to the piston pin of the piston, a lower link connected to the other end of the upper link and connected to the crank pin of the crankshaft, and one end connected to the lower link, the other A variable stroke characteristic engine that has a variable stroke link mechanism consisting of a control link whose end is swingably connected to a control shaft, and that makes the moving stroke of the piston variable by driving a vane hydraulic actuator provided on the control shaft. It is publicly known (see Patent Document 1 below).
JP-A-2005-76555

  By the way, in such a variable stroke characteristic engine, a vane type hydraulic actuator is used to drive the variable stroke link mechanism. This actuator has a cylindrical housing that houses a vane shaft, a vane oil chamber, and the like. Since the occupying volume in the direction is relatively large, if this actuator is provided in the crank chamber, there is a problem that the engine becomes large, especially the height becomes large. If this is supported by a member having high rigidity, the above problem becomes more prominent, and when this engine is used for an automobile, the height of the engine room must be increased.

  SUMMARY OF THE INVENTION The present invention has been made in view of the above circumstances, and is a vane hydraulic pressure in a novel variable stroke characteristic engine that solves the problem by suppressing the increase in size of the engine in the height direction and increasing its supporting rigidity. An object is to provide an actuator mounting structure.

In order to achieve the above object, according to the present invention, a piston and a crankshaft are connected to a control shaft via a stroke variable link mechanism, and the crankshaft is connected to the control shaft in a crank chamber of the engine body. The vane type hydraulic actuator is provided in a variable stroke characteristic engine in which a vane type hydraulic actuator disposed below is provided, and the control shaft is driven by the hydraulic actuator to operate the stroke variable link mechanism to change the moving stroke of the piston. Structure,
The vane-type hydraulic actuator includes a housing, a vane shaft integrated with a control shaft rotatably provided in the housing, and a pair of protrusions integrally provided on the outer peripheral surface of the vane shaft with an interval in the circumferential direction. A pair of vane oil chambers provided between the housing and the vane shaft so that each of the pair of vanes is accommodated in a circumferentially movable manner, and the pair of vane oil chambers in the circumferential direction. A pair of partition portions provided in the housing between the vane oil chambers so as to partition into,
The pair of vane oil chamber, in the projection plane in the axial direction of the crankshaft, the disposed side by side in a direction orthogonal to the stroke characteristic cylinder axis of the variable engine of the engine body Rutotomoni, the pair of partition portions, Arranged side by side in the direction along the cylinder axis, the housing of the vane type hydraulic actuator is supported by a housing receiving portion provided integrally with a bearing block that supports the control shaft, and in a partition between the vane oil chambers, The housing is fastened to the housing receiving portion by a fastening member .

In order to achieve the above object, according to a second aspect of the present invention, in the first aspect, the cylinder axis of the engine body is inclined to one side with respect to a vertical line, and the crankcase of the engine body is provided. Is extended to one side of the cylinder block, and the vane type hydraulic actuator is accommodated in the crank chamber of the extended portion .

According to the first aspect of the present invention, the pair of vane oil chambers of the vane type hydraulic actuator are arranged side by side in a direction orthogonal to the cylinder axis of the stroke characteristic variable engine on the axial projection surface of the crankshaft . Therefore, the height of the actuator can be shortened, and thereby the increase in size of the engine in the height direction can be suppressed.

The housing of the base over emissions hydraulic actuators, the partition portion between the vane oil chamber, since it is fastened by a fastening member to said housing receiving, it is possible to improve the support rigidity of the housing, the upper housing The height of the support portion can be shortened, whereby the increase in size of the engine in the height direction can be further suppressed.

Furthermore, according to the second aspect of the present invention, it is possible to suppress an increase in the size of the engine body in the height direction, and to secure the degree of freedom of the engine tilt range.

  DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments of the present invention will be specifically described below based on examples of the present invention shown in the accompanying drawings.

  First, a first embodiment of the present invention will be described with reference to FIGS.

  1 is a schematic overall perspective view of a variable stroke characteristic engine, FIG. 2 is a view taken in the direction of arrow 2 in FIG. 1, FIG. 3 is a cross-sectional view taken along line 3-3 in FIG. 1 is a sectional view taken along line 4-4 in FIG. 1 (low compression ratio state), FIG. 5 is a sectional view taken along line 5-5 in FIG. 2, and FIG. 6 is a sectional view taken along line 6-6 in FIG. 7 is an enlarged vertical view taken along line 7-7 in FIG. 5, FIG. 8 is a sectional view taken along line 8-8 in FIG. 3, and FIG. 9 is a perspective view taken along arrow 9 in FIG. FIG. 10 is an exploded perspective view of the vane hydraulic actuator, and FIG. 11 is a hydraulic circuit diagram of a control system of the vane hydraulic actuator.

  1 to 4, a variable stroke characteristic engine E according to the present invention is for an automobile and is placed horizontally in an engine room of an automobile (not shown) (the crankshaft 30 is arranged laterally with respect to the traveling direction of the automobile). ). When the engine E is mounted on a vehicle, as shown in FIG. 2, the cylinder is slightly tilted backward, that is, its cylinder axis LL is slightly tilted backward with respect to the vertical line V-V.

Further, the stroke characteristic variable engine E is an OHC type four-cycle engine of the series 4-cylinder, the engine body 1 includes a cylinder block 2 which has four cylinders 5 eclipsed set side by side in the lateral direction, the cylinder block 2 The cylinder head 3 is integrally coupled to the deck surface of the cylinder block 3 via the gasket 6, the upper block 40 (upper crankcase) is integrally formed at the lower portion of the cylinder block 2, and the lower is integrally coupled to the lower surface thereof. A block 41 (lower crankcase) is provided, and the crankcase 4 is formed by the upper block 40 and the lower block 41. A head cover 9 is integrally crowned on the upper surface of the cylinder head 3 via a sealing material 8, and an oil pan 10 is integrally coupled to the lower surface of the lower block 41 (lower crankcase). .

  Pistons 11 are slidably fitted to the four cylinders 5 of the cylinder block 2, and four combustion chambers 12 are provided on the lower surface of the cylinder head 3 facing the top surfaces of the pistons 11. An intake port 14 and an exhaust port 15 communicating with those combustion chambers 12 are formed. An intake valve 16 is provided in the intake port 14 and an exhaust valve 17 is provided in the exhaust port 15 so as to be opened and closed. On the cylinder head 3, a valve operating mechanism 18 for opening and closing the intake valve 16 and the exhaust valve 17 is provided. The valve mechanism 18 swings on an intake side cam shaft 20 and an exhaust side cam shaft 21 that are rotatably supported by the cylinder head 3, and on an intake side and exhaust side rocker shafts 22, 23 provided on the cylinder head 3. The intake side and exhaust side camshafts 20 and 21 and the intake side and exhaust side rocker arms 24 and 25 connected to the intake valve 16 and the exhaust valve 17 so as to be pivotally supported are provided. According to the rotation of the shafts 20 and 21, the intake side and exhaust side rocker arms 24 and 25 are swung against the valve closing force of the valve springs 26 and 27 to open and close the intake valve 16 and the exhaust valve 17 at a predetermined timing. Can be operated.

  As shown in FIG. 2, the intake-side and exhaust-side camshafts 20, 21 are interlocked with a crankshaft 30 described later via a conventionally known timing transmission mechanism 28, and according to the rotation of the crankshaft 30, It is driven at half the rotational speed. The valve mechanism 28 is covered with a head cover 9 that is integrally crowned on the cylinder head 3. The cylinder head 3 is provided with a cylindrical plug insertion cylinder 31 corresponding to the four cylinders, and a spark plug 32 is inserted into the plug insertion cylinder 31.

  The plurality of intake ports 14 corresponding to the four cylinders 5 are opened toward the front surface of the engine body 1, that is, the front side of the vehicle, and an intake manifold 34 of the intake system IN is connected thereto. Since the intake system IN has a conventionally known structure, a detailed description thereof will be omitted.

  A plurality of exhaust ports 15 corresponding to the four cylinders 5 are opened toward the rear surface of the engine body 1, that is, toward the rear side of the vehicle, and an exhaust manifold 35 of the exhaust system EX is connected thereto. Since the exhaust system EX has a conventionally known structure, a detailed description thereof is omitted.

  As shown in FIGS. 3 and 4, the crankcase 4 including the upper block 40 (upper crankcase) at the lower part of the cylinder block 2 and the lower block 41 (lower crankcase) is more forward than the cylinder 5 part of the cylinder block 2. A variable stroke link mechanism LV (described later) and a vane hydraulic actuator that drives the variable stroke link mechanism LV are provided in the crank chamber CC of the extended portion 36 so as to make the moving stroke of the piston 11 variable. AC (described later) is provided.

  As shown in FIGS. 2, 3 and 5, 6, a lower block 41 is fixed to the lower surface of the upper block 40 integrally formed at the lower portion of the cylinder block 2 with a plurality of connecting bolts 42. The journal shaft 30J of the crankshaft 30 is rotatably supported by a plurality of journal bearing portions 43 formed on the mating surfaces of the upper block 40 and the lower block 41 (see FIG. 8).

  As shown in FIG. 5, the lower block 41 is cast and molded in a closed cross-sectional structure having a square shape in plan view. End bearing members 50 and 51 are provided at the left and right ends thereof, and an intermediate portion thereof is provided at In the center of the left and right intermediate bearing members 52 and 53, a central bearing member 54 (a housing HU described later is integrally formed) is provided as a bearing cap. The journal shaft 30J of the crankshaft 30 is supported.

  As shown in FIGS. 5, 6, and 9, the central bearing member 54 as the bearing cap is cast and formed separately from the lower block 41, and is firmly fixed to the lower block 41 by a plurality of connecting bolts 56. The central bearing member 54 is also firmly fixed to the lower surface of the upper block 40 by other connecting bolts 57. One side portion of the central bearing member 54 that is biased from the bearing portion 54A of the crankshaft 30 to the one side (front side of the engine main body 1) is an enormous portion 58 having an enlarged vertical width and a large thickness. A housing HU of a vane type hydraulic actuator AC, which will be described later in detail, is cast and formed in the enormous portion 58.

  Next, the structure of the variable stroke link mechanism LV that makes the moving stroke of the pistons 1 variable will be described mainly with reference to FIGS. 3 and 4. The support surface of the upper block 40 and the lower block 41 is rotatably supported. An intermediate portion of a triangular lower link 60 is pivotally connected to a plurality of crank pins 30P of the crankshaft 30 so as to be swingable. One end (upper end) of the lower link 60 is pivotally connected to the lower end (large end) of an upper link (connecting rod) 61 pivotally connected to the piston pin 13 of the piston 11 via a first connecting pin 62. The upper end of the control link 63 is pivotally connected to the other end (lower end) of each lower link 60 via the second connecting pin 64. The control link 63 extends downward, and an eccentric pin 65P of a control shaft 65 (detailed later) is pivotally connected to the lower end of the control link 63. The control shaft 65 is provided with a vane type hydraulic actuator AC (described later in detail) coaxially therewith, and the control shaft 65 is rotated within a predetermined angle range (about 90 degrees) by driving the vane type hydraulic actuator. The control link 63 is driven to swing by the phase shift of the eccentric pin 65P. Specifically, the control shaft 65 rotates between a first position shown in FIG. 3 (the eccentric pin 65P is a lower position) and a second position shown in FIG. 4 (the eccentric pin 65P is a left position). Is possible. 3, since the eccentric pin 65P of the control shaft 63 is positioned below, the control link 63 is pulled down and the lower link 60 swings around the crank pin 30P of the crankshaft 30 in the clockwise direction. As a result, the upper link 61 is pushed up, and the position of the piston 11 becomes higher than the cylinder 5, and the engine E enters a high compression ratio state. On the other hand, in the second position shown in FIG. 4, the eccentric pin 65P of the control shaft 65 is located to the left (higher than the first position), so that the control link 63 is pushed up to lower link 60. Swings counterclockwise around the crank pin 30P of the crankshaft 30, the upper link 61 is pushed down, and the position of the piston 11 is lowered with respect to the cylinder 5, and the engine E enters a low compression ratio state. As described above, by the rotation control of the control shaft 65, the control link 63 swings, the motion constraint condition of the lower link 60 changes, and the stroke characteristics including the top dead center position of the piston 11 change. It becomes possible to arbitrarily control the compression ratio of the engine E.

  Accordingly, the upper link 61, the first connecting pin 62, the lower link 60, the second connecting pin 64, and the control link 63 constitute a variable stroke link mechanism LV according to the present invention.

  As shown in FIGS. 6, 7, 9, and 10, the control shaft 65 that is connected to the control link 63 and operates the stroke variable link mechanism LV includes a plurality of journal shafts 65 </ b> J and eccentric pins 65 </ b> P, like the crank shaft 30. Are alternately connected via an arm 65A to form a crank shape, and a cylindrical vane shaft 66 of a vane type hydraulic actuator AC is coaxially and integrally provided at the center in the axial direction. The eccentric pins 65P of the control shaft 65 are directly fixed to the eccentric positions on both side surfaces of the 66. The control shaft 65 is provided to be biased to one side of the lower block 41 (the front side of the engine body 1), and the journal shaft 65J is fixed to the lower block 41 and a plurality of connecting bolts 68 on the lower surface thereof. The bearing block 70 is rotatably supported.

  As shown in FIGS. 6, 7, and 9, the bearing block 70 that supports the control shaft 65 includes a connecting member 71 that extends in the axial direction of the control shaft 65, and an interval in the longitudinal direction of the connecting member 71. A plurality of bearing walls 72 that are integrally connected upright and a housing receiving portion 73 provided at a central portion in the longitudinal direction of the connecting member 71, and is cast into a block shape so as to ensure high rigidity, By bearing portions formed on the mating surfaces of the upper surfaces of the plurality of bearing walls 72 and the lower surfaces of the bearing walls 50a, 51a, 52a, 53a extended from the bearing members 50, 51, 52, 53 of the lower block 40, As described above, the plurality of journal shafts 65J of the control shaft 65 are rotatably supported. Further, as shown in FIG. 7, the housing receiving portion 73 is formed in a concave shape downward in a direction away from the housing HU, and a concave portion G is formed above the concave portion G. The vane hydraulic actuator AC is formed in the concave portion G. The lower portion of the housing HU is received, and the lower portion of the housing HU is fastened on the housing receiving portion 73 by a fastening member, that is, a plurality of fastening bolts 74. Therefore, the housing HU of the hydraulic actuator AC is integrally fastened and supported on the bearing block 70 that supports the control shaft 65.

  As will be described in detail later, the plurality of fastening bolts 74 fasten the housing HU and the central housing receiving portion 73 between the pair of vane oil chambers 86 of the vane hydraulic actuator AC.

Incidentally, since the housing HU of the actuator AC is integrally fastened to the highly rigid bearing block 70, the rigidity of the housing HU itself is increased, and a recess G is formed in the housing receiving portion 73 of the bearing block 70, as accommodation space this recess G, by the lower housing HU is accommodated therein, the actuator AC is made can be mounted in a compact with a high rigidity to the engine body 1, which contributes to downsizing of the engine E itself be able to.

  As shown in FIGS. 6, 7, 9, and 10, the vane hydraulic actuator AC provided coaxially with the control shaft 65 is provided in the crank chamber CC of the engine body 1 below the crankshaft 30. The housing HU is provided in the enormous portion 58 on one side of the central bearing member 54 (fixed integrally with the upper block 40 and the lower block 41) as the bearing cap. A short cylindrical vane chamber 80 whose both end faces are open is formed in the central portion of the housing HU in the axial direction. In the vane chamber 80, the vane shaft 66 integral with the control shaft 65 is accommodated, and a pair of a pair of phase difference of about 180 ° exists at the axially central portion of the outer peripheral surface of the vane shaft 66. A vane 87 protrudes integrally. The left and right side portions (slightly smaller in diameter than the central portion) of the vane shaft 66 are fixed to the both sides of the housing HU with a plurality of bolts 83, and the left and right vane bearing portions 81, 82, serving as the other housings 81, 82, 82 is rotatably supported via a surface bearing. The opening side surface of the housing HU is closed by the vane bearing portions 81 and 82. A pair of fan-shaped vane oil chambers 86 are defined between the inner peripheral surface of the vane chamber 80 and the outer peripheral surface of the vane shaft 66 with a phase difference of about 180 °. In the pair of vane oil chambers 86, a pair of vanes 87 projecting integrally from the outer peripheral surface of the vane shaft 66 are accommodated, respectively, and the outer peripheral surfaces are connected to the inner peripheral surface of the vane oil chamber 86 via packing. The vanes 87 are in sliding contact with each other, and each fan-shaped vane oil chamber 86 is oil-tightly divided into two control oil chambers 86a and 86b.

Meanwhile, as shown in FIG. 6, the projection plane in the axial direction of the crank shaft 30, below the crankshaft 30, a pair of vane oil chamber 86 in the housings HU is the cylinder axis L-L of the engine body 1 The vane shafts 66 are arranged side by side in a direction orthogonal to the pair, and the pair of partition portions are arranged in a direction along the cylinder axis LL so as to partition the pair of vane oil chambers 86. ing. Thereby, the height of the housing H is substantially shorter than the lateral width D. The lower portion of the housing HU is fastened to the housing receiving portion 73 of the bearing block 70 by a fastening member, that is, a plurality of fastening bolts 74, between the pair of vane oil chambers 86. Therefore, it is possible to shorten the vertical width between the housing HU and the housing receiving portion 73 and fasten them with the fastening bolts 74. Therefore, the vane hydraulic actuator AC can be supported on the engine body 1 with its height H shorter than its lateral width D, and the housing HU can be reduced in vertical width with respect to the housing receiving portion 73. The housing receiving portion 73 can be firmly fastened.

  The housing HC of the vane hydraulic actuator AC that drives the control shaft 65 uses a central bearing member (formed separately from the lower block 41 and fixed thereto) as a bearing cap of the lower block 41. It is possible to reduce the number of parts, and the volume occupied by the housing HC in the crank chamber CC can be reduced, and an increase in the bulk of the crankcase can be suppressed.

  As shown in FIGS. 5, 7, and 9, the upper surface of the housing HU formed on the central bearing member 54 is flat and spreads in a dovetail shape from the bearing portion 54 </ b> A of the crankshaft 30 toward the end on the housing HU side. As shown in FIG. 7, the width D1 of the mounting surface 90 in the direction of the control shaft 65 is wider than the width D2 of the housing HU. A valve unit 92 that accommodates the electromagnetic valve V (FIG. 11) of the hydraulic circuit of the vane hydraulic actuator AC is fixedly supported by a plurality of bolts 91, and the valve unit 92 passes through the wall surface of the cylinder block 2. It is arranged on the upper surface in an exposed state (see FIG. 1).

  As described above, the valve unit 92 is firmly fixed on the mounting surface of the housing HU, and the valve unit 92 is on the mounting wall surface of the cylinder block 2, and the four sides are open. The switching operation and maintenance of the valve unit 92 are facilitated.

  Next, a hydraulic circuit of the vane type hydraulic actuator AC that drives and controls the stroke variable link mechanism LV will be described with reference to FIG.

  As described above, the inside of the pair of fan-shaped vane oil chambers 86 formed by the vane shaft 66 of the control shaft 65 and the housing HU is divided into two control oil chambers 86a and 86b by the vanes 87, respectively. The control oil chambers 86a and 86b are connected to the oil tank T via a hydraulic circuit described later. An oil pump P driven by a motor M, a check valve C, an accumulator A, and an electromagnetic switching valve V are connected to the hydraulic circuit. An oil tank T, a motor M, an oil pump P, a check valve C, and an accumulator A constitute a hydraulic pressure supply device S, which is provided at an appropriate position of the engine body 1, and an electromagnetic switching valve V is provided inside the valve unit 92 described above. Is provided. The hydraulic pressure supply device S and the electromagnetic switching valve V are connected by two pipes P1 and P2, and the electromagnetic switching valve V and the control oil chambers 86a and 86b of the vane hydraulic actuator AC are two pipes P3 and P4. Connected with. Therefore, in FIG. 11, when the electromagnetic switching valve V is switched to the right position, the hydraulic oil generated by the oil pump P is supplied to the control oil chamber 86a, and the vane 87 is pushed by the hydraulic pressure, and the control shaft 65 is counterclockwise. The hydraulic oil generated by the oil pump P, which rotates in the direction and conversely switches the electromagnetic switching valve V to the left position, is supplied to the control oil chamber 86b, and the vane 87 is pushed by the hydraulic pressure to rotate the control shaft 65 clockwise. , The phase of the eccentric pin 65P of the control shaft 65 changes. As described above, the control link 63 of the variable stroke link mechanism LV is pivotally connected to the eccentric pin 65P of the control shaft 65 so that the control shaft 65 can be swung. The stroke variable link mechanism LV is operated by the phase change of the eccentric pin 65P.

  By the way, according to the first embodiment, the pair of vane oil chambers 86 are arranged side by side in a direction orthogonal to the cylinder axis LL of the engine main body 1, so that the height of the actuator housing is shortened. Thus, it is possible to suppress an increase in the size of the engine in the height direction.

The housing HU of the vane hydraulic actuator AC is a partition between a pair of vane oil chambers 86 arranged side by side in a direction orthogonal to the cylinder axis LL , and is fastened to the housing receiver 73 by a fastening member 74. Since it is fastened, the height of the support part of the housing HU can also be shortened, whereby the size of the engine E in the height direction can be further suppressed.

  Furthermore, the engine body can be prevented from being enlarged in the height direction, and the degree of freedom of the engine tilt range can be secured.

  Next, a second embodiment of the present invention will be described with reference to FIG.

  FIG. 12 is a vertical side view of a part of the engine body 1, and the same reference numerals are given to the same elements as those in the first embodiment.

  In the second embodiment, when the engine E is mounted on an automobile, it is arranged in a slightly forward tilted posture, that is, in a state where its cylinder axis LL is slightly inclined forward with respect to the vertical line V-V. The crankcase 4 of the engine body 1 projects forward from the cylinder barrel portion, and a vane hydraulic actuator AC is accommodated in the crank chamber CC of the projecting portion. The actuator AC is located below the crankshaft 30. As in the first embodiment, the pair of vane oil chambers 86 supported by the engine body 1 and formed in the housing HU are arranged side by side in a direction orthogonal to the cylinder axis LL, and the housing HU. The lower part is fastened to the housing receiver 73 of the bearing block 70 by a fastening member, that is, a plurality of fastening bolts 74, between the pair of vane oil chambers 86.

  Therefore, the second embodiment can also suppress the increase in size of the engine E in the height direction, can improve the support rigidity of the housing HU, and can shorten the front-rear width of the engine E. .

  Next, a third embodiment of the present invention will be described with reference to FIG.

  FIG. 13 is a vertical side view of a part of the engine main body 1, and the same reference numerals are given to the same elements as those in the first embodiment.

  In the third embodiment, when the engine E is mounted on an automobile, it is slightly rearwardly inclined as in the first embodiment, that is, its cylinder axis LL is inclined slightly backward with respect to the vertical line V-V. Placed in a state. The crankcase 4 of the engine body 1 projects rearward from the cylinder barrel portion, and a vane hydraulic actuator AC is accommodated in the crank chamber CC of the projecting portion. The actuator AC is located below the crankshaft 30. As in the first embodiment, the pair of vane oil chambers 86 supported by the engine body 1 and formed in the housing HU are arranged side by side in a direction orthogonal to the cylinder axis LL, and the housing HU. The lower part is fastened to the housing receiver 73 of the bearing block 70 by a fastening member, that is, a plurality of fastening bolts 74, between the pair of vane oil chambers 86.

  Accordingly, the third embodiment can also suppress the increase in size of the engine E in the height direction, can improve the support rigidity of the housing HU, and can shorten the front-rear width of the engine E. .

  Next, a fourth embodiment of the present invention will be described with reference to FIG.

  FIG. 14 is a cross-sectional view of the vane type hydraulic actuator corresponding to FIG. 6 of the first embodiment, and the same reference numerals are given to the same elements as in the first embodiment.

  In this fourth embodiment, the oil passage structure formed in the vane type hydraulic actuator is different from that of the first embodiment. That is, the oil passage on the lower side of the vane shaft 66 is abolished and the upper portion of the vane shaft 66 is disposed. This is a case where an oil supply passage is formed only in the housing HU. As shown in FIG. 14, two communicating oil passages 98 and 99 are formed in the vane shaft 66 in a cross shape in a radial direction by shifting in the axial direction. One communication oil path 98 communicates a pair of control oil paths 86b with each other, and the other communication oil path 99 communicates a pair of control oil paths 86a with each other. Thereby, the oil path formed in the lower part of the housing HU can be abolished, and the rigidity of the lower part of the housing HU can be further improved.

  As mentioned above, although the Example of this invention was described, this invention is not limited to the Example, A various Example is possible within the scope of the present invention.

  For example, in the above embodiment, the case where the vane hydraulic actuator mounting structure of the present invention is applied to a variable compression ratio engine that changes the top dead position of the piston by the phase change of the eccentric pin of the control shaft has been described. This can also be applied to other stroke characteristic variable engines. Moreover, although the said Example demonstrated the case where this invention was applied to the engine horizontally installed in a vehicle, of course, this can be applied also to the engine vertically installed in a vehicle.

Schematic overall perspective view of engine with variable stroke characteristics 2 arrow view of FIG. Sectional view along line 3-3 in FIG. 1 (high compression ratio state) Sectional view along line 4-4 in FIG. 1 (low compression ratio state) Sectional view along line 5-5 in FIG. Cross-sectional view along line 6-6 in FIG. Enlarged vertical view along line 7-7 in FIG. Sectional view along line 8-8 in FIG. 9 perspective view of FIG. Disassembled perspective view of vane hydraulic actuator Hydraulic circuit diagram of hydraulic actuator control system A longitudinal side view of a part of the variable stroke characteristics engine A longitudinal side view of a part of the variable stroke characteristics engine Sectional drawing of the vane type hydraulic actuator corresponding to FIG. 6 of the first embodiment

1 ... Engine body 2 ... Cylinder block 4 ... Crankcase 11 ... Piston 30 ... Crankshaft 65 ······························································································· Housing 74 .... Fastening member (fastening bolt)
86 ... Vane oil chamber 87 ... Vane E ... Variable stroke characteristics engine AC ... Vane hydraulic actuator CC ... ... Crank chamber LV ..... Stroke variable link mechanism HU ..... Housing LL ..... Cylinder axis VV ..... Vertical line

Claims (2)

The piston (11) and the crankshaft (30) are connected to the control shaft (65) via a variable stroke link mechanism (LV), and the crankshaft (CC) of the engine body (1) is connected to the control shaft (65). ) Is provided with a vane type hydraulic actuator (AC) disposed below the crankshaft (30), and the hydraulic actuator (AC) drives the control shaft (65) to operate the variable stroke link mechanism (LV). A vane type hydraulic actuator mounting structure in a variable stroke characteristic engine in which the moving stroke of the piston (11) is variable,
The vane hydraulic actuator (AC) includes a housing (HU), a vane shaft (66) integral with a control shaft (65) rotatably provided in the housing (HU), and an outer periphery of the vane shaft (66). A pair of vanes (87) provided integrally on the surface with an interval in the circumferential direction, and a pair of vanes (87) provided between the housing (HU) and the vane shaft (66). ) Between each of the vane oil chambers (86) so as to divide the pair of vane oil chambers (86) in the circumferential direction. And a pair of partition portions provided in the housing (HU),
The pair of vane oil chambers (86) is located on the axial projection surface of the crankshaft (30) with respect to the cylinder axis (LL) of the engine body (1) of the variable stroke characteristic engine (E). Rutotomoni are arranged side by side in a direction orthogonal, the pair of partition portions are arranged side by side in the direction along the cylinder axis (L-L),
A housing (HU) of the vane hydraulic actuator (AC) is supported by a housing receiving portion (73) provided integrally with a bearing block (70) that supports the control shaft (65), and the vane oil chamber (86). ), The housing (HU) is fastened to the housing receiving portion (73) by a fastening member (74) , and the vane hydraulic actuator mounting structure in the variable stroke characteristic engine. The cylinder axis (LL) of the engine body (1) is inclined to one side with respect to the vertical line (V-V), and the crankcase (4) of the engine body (1) is a cylinder block ( 2. The stroke characteristic according to claim 1 , wherein the vane type hydraulic actuator (AC) is housed in a crank chamber (CC) of the projecting portion. Mounting structure of vane type hydraulic actuator in variable engine.

Images