JP4815312B2 - 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 stroke variable link mechanism, and a vane type hydraulic actuator is provided on the control shaft, and the control shaft is driven by this actuator to operate the variable stroke link mechanism. The present invention relates to a mounting structure of a vane type hydraulic actuator in a variable stroke characteristic engine in which a moving stroke of a piston is variable.

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 housing that houses a vane shaft, a vane oil chamber, and the like, and occupies a radial direction. Since the volume is relatively large and it is connected to the crankshaft via a variable stroke link mechanism, if this actuator is provided in the crank chamber, the engine body becomes larger in the width direction, that is, in the direction across the crankshaft. Furthermore, in order to increase the support rigidity of this actuator, if it is supported by a member having high rigidity, the above problem becomes more prominent. When this engine is used for an automobile, The width in the front-rear direction (when the engine is installed horizontally) or the width in the left-right direction For longitudinally arranged engine) it is forced to expand.

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

In order to achieve the above object, according to the first aspect of the present invention, a piston and a crankshaft are connected to a control shaft via a variable stroke link mechanism disposed on the side of the crankshaft. A vane type hydraulic actuator is installed on a variable stroke characteristic engine in which a variable stroke characteristic mechanism is provided in which a variable stroke moving mechanism of the piston is operated by driving a control shaft by this hydraulic actuator and operating the variable stroke link mechanism. Because
The vane hydraulic actuator includes a housing, a vane shaft integrally formed with a control shaft rotatably provided in the housing, and a vane protruding from an outer peripheral surface, and a pair of vanes accommodated between the housing and the vane shaft. A vane oil chamber,
The housing is provided in a crankcase, is fixed to the crankcase and supports both the crankshaft and the control shaft, and the pair of vane oil chambers is provided for the engine body of the variable stroke characteristic engine. Arranged side by side in the cylinder axis direction, the housing and the crankcase are fastened by a plurality of lateral fastening members from the direction orthogonal to the cylinder axis of the engine body on both sides thereof, and at least some of the fastening members are It is characterized by being provided between a pair of vane oil chambers arranged in the cylinder axial direction.

To achieve the above object, according to a second aspect of the present invention, in the first aspect of the present invention, the actuator housing and the cover member covering the opening of the housing are provided with a plurality of crankshafts extending in the crankshaft direction. It is fastened by a direction fastening member, and a part of these crankshaft direction fastening members is provided between the lateral fastening members.

In order to achieve the above object, according to a third aspect of the present invention, in the first or second aspect, the hydraulic passage for supplying hydraulic oil to the pair of vane oil chambers includes the lateral fastening member and the crankshaft. It is characterized in that it is provided in the housing by shifting in the direction.

In order to achieve the above object, according to a fourth aspect of the present invention, in the first, second, or third aspect, the cylinder axis of the engine body is inclined to one side with respect to a vertical line. On the other side, the vane type hydraulic actuator is provided in a crankcase below the crankshaft.

  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 the cylinder axial direction of the engine body of the variable stroke characteristic engine, so that the direction perpendicular to the crankshaft of the engine The enlargement of the width can be suppressed.

Moreover, the housing and the crankcase are fastened by a plurality of lateral fastening members from the direction orthogonal to the cylinder axis of the engine body on both sides thereof, and at least a part of those fastening members are arranged in the cylinder axial direction. Since it is provided between the pair of vane oil chambers, the housing and the crankcase can improve the support rigidity of the vane hydraulic actuator while suppressing the increase in the lateral width of the engine.

According to the second aspect of the present invention, the housing of the actuator and the cover member covering the opening of the housing are fastened by the plurality of crankshaft direction fastening members extending in the crankshaft direction. Since a part of the member is provided between the lateral fastening members, it is possible to improve the fastening rigidity of the housing of the actuator while suppressing an increase in the lateral width of the engine.

Further, according to the invention of claim 3, the hydraulic passage for supplying the hydraulic oil to the pair of vane oil chambers is provided in the housing so as to be shifted in the crankshaft direction from the lateral fastening member. And the hydraulic passage can be provided close to each other, and the suppression of enlargement in the width direction of the engine becomes more remarkable.

Furthermore, according to the invention of claim 4 , the cylinder axis of the engine body is inclined to one side with respect to the vertical line, and on the other side, the actuator is placed in the crankcase below the crankshaft. Thus, the actuator can be arranged by effectively utilizing the dead space that can be secured in the crankcase, and both the increase in the width of the engine and the increase in the height thereof can be suppressed.

  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.

  The variable stroke characteristic engine E is an in-line four-cylinder OHC type four-cycle engine. The engine body 1 includes a cylinder block 2 in which four cylinders 5 are arranged side by side, A cylinder head 3 integrally coupled to the deck surface via a gasket 6, an upper block 40 (upper crankcase) integrally formed at the lower portion of the cylinder block 2, and a lower block integrally coupled to the lower surface thereof 41 (lower crankcase), and the upper block 40 and the lower block 41 form the crankcase 4. 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, and this actuator AC is disposed below the crankshaft 30.

  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. The central bearing member 54 is firmly fixed to the lower block 41 constituting the crankcase 4 by a plurality of lateral fastening members, that is, lateral fastening bolts 56, from a direction orthogonal to the cylinder axis LL. . As shown in FIG. 6, some of the plurality of lateral fastening members 56 are positioned between a pair of vertical vane oil chambers 86 provided in a housing HU of a vane actuator AC described later. . The central bearing member 54 is also firmly fixed to the lower surface of the upper block 40 by other fastening bolts 57.

  As shown most clearly in FIG. 9, one side portion of the central bearing member 54 as a bearing cap that is biased to one side (front of the engine body 1) from the bearing portion 54 </ b> A of the crankshaft 30 extends the vertical width. The enormous portion 58 is thick, and a housing HU of a vane type hydraulic actuator AC, which will be described in detail later, is formed on the enormous portion 58.

  Next, the structure of the stroke variable link mechanism LV that makes the moving stroke of the piston 11 variable will be described mainly with reference to FIGS. 3 and 4. The crankcase 4, that is, the mating surface of the upper block 40 and the lower block 41. An intermediate portion of a triangular lower link 60 is pivotally connected to each of the plurality of crank pins 30P of the crankshaft 30 rotatably supported by each other. 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) on the same axis. The control shaft 65 is driven within a predetermined angle range (about 90 degrees) by driving the vane type hydraulic actuator AC. The control link 63 is oscillated and driven 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 63P 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 below the crankshaft 30 so as to be biased toward one side of the lower block 41 (the front side of the engine body 1). The journal shaft 65J has a plurality of lower blocks 41 and a plurality of lower surfaces thereof. A bearing block 70 fixed by a connecting bolt 68 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.

  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, By accommodating the recess G as a storage space and the lower part of the housing HU being stored therein, the actuator AC can be mounted on the engine body 1 with high rigidity and compactly, 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 huge portion 58 on one side of a 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. A vane shaft 66 integral with the control shaft 65 is accommodated in the vane chamber 80, and a pair of vanes exist with a phase difference of about 180 ° in the axial center of the outer peripheral surface of the vane shaft 66. 87 protrudes integrally. Also, the left and right side portions (slightly smaller in diameter than the central portion) of the vane shaft 66 are fixed to the opening portions on both sides of the housing HU by a plurality of fastening members, that is, fastening bolts 83, at the outer peripheral portion of the vane chamber 80. The annular left and right cover members 81 and 82 (left and right vane bearing portions) are rotatably supported via surface bearings. The opening side surface of the housing HU is closed by left and right cover body members 81 and 82.

  As shown in FIGS. 6 and 7, the plurality of fastening members 83 are provided along the axial direction of the crankshaft 30 to constitute a crankshaft direction fastening member. Is provided so as to cross between the transverse fastening members 56.

  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 °. As shown in FIG. 6, the pair of vane oil chambers 87 are arranged in the vertical direction with the vane shaft 66 interposed therebetween, that is, in the direction of the cylinder axis LL, thereby forming the actuator AC in the housing HU. In the vane chamber 80, the width D4 in the lateral direction (direction perpendicular to the cylinder axis LL) is shorter than the width D3 in the vertical direction.

  As shown in FIGS. 6 and 7, a pair of vane 87 projecting integrally from the outer peripheral surface of the vane shaft 66 is accommodated in the pair of vane oil chambers 86, respectively. Each vane 87 divides each fan-shaped vane oil chamber 86 into two control oil chambers 86a and 86b in an oil-tight manner. In the housing HU, hydraulic oil passages 88 and 89 communicating with the control oil chambers 86a and 86b are formed by shifting their positions in the direction of the lateral fastening member 56 and the crankshaft 30, and these hydraulic passages 88 and 89 are provided. Is connected to an electromagnetic valve V in a valve unit 92 described later. These hydraulic passages 88 and 89 are allowed to overlap each other when viewed from the lateral fastening member 56 and the crankshaft 30 direction. Further, by providing the hydraulic passages 88 and 89 on the inner side of the crankcase 4, that is, at a position close to the crankshaft 30, the size of the engine E in the width direction can be suppressed.

  As shown in FIGS. 5, 7, and 9, the upper surface of the housing HU formed in the central bearing member 54 as a bearing cap has a dovetail from the bearing portion 54 </ b> A of the crankshaft 30 toward the end portion on the housing HU side. As shown in FIG. 7, the width D1 in the direction of the control shaft 65 of the mounting surface 90 is wider than the width D2 in the same direction of the housing HU. A valve unit 92 that accommodates a solenoid valve V (FIG. 11) of the hydraulic circuit of the vane hydraulic actuator AC is fixedly supported on the mounting surface 90 with a plurality of bolts 91. The valve unit 92 is a cylinder block. It penetrates the wall surface of 2 and is arrange | positioned in the exposed state on the upper surface (refer 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 is open on all four sides. 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 pair of fan-shaped vane oil chambers 86 formed in the vertical direction by the vane shaft 66 of the control shaft 65 and the housing HU are partitioned 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 hydraulic passages formed in the housing HU. 88 and 89 are connected. 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. When the electromagnetic switching valve V is switched to the left position, the hydraulic oil generated by the oil pump P is supplied to the control oil chamber 86b, and the vane 87 is pushed by the hydraulic pressure so that the control shaft 65 is turned clockwise. By rotating in the direction, 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 this embodiment, since the pair of vane oil chambers 86 are arranged side by side in the cylinder axis LL direction of the engine body 1, the actuator AC has a substantially lateral width D4 in the vertical direction. As a result, the width of the engine E in the lateral direction perpendicular to the crankshaft 30 is shortened, and an increase in size in the same direction is suppressed.

  Further, if an engine accessory (not shown) is provided outside the crankcase 4 provided with the actuator AC, the engine on the other side (front) of the engine E inclined to one side (rear) will be described. It is easy to dispose the engine accessory above, and the pair of vane oil chambers 86 of the actuator AC are arranged side by side in the axial direction of the cylinder 5, so that the engine accessory can be disposed close to the actuator AC.

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

  FIG. 12 is a longitudinal sectional view of a vane type hydraulic actuator corresponding to FIG. 6 in the first embodiment, and the same reference numerals are given to the same elements as in the first embodiment.

  In this 2nd Example, the fastening structure with respect to the lower block 41 of the center bearing member 54 as a bearing cap in which the vane type hydraulic actuator AC is provided is slightly different. Of the plurality of lateral fastening members 56 that fasten the central bearing member 54 to the lower block 41, the two lateral fastening members 56 positioned between the pair of vane oil chambers 86 avoid the vane oil chamber 86. Thus, it is possible to use a long fastening portion (screw fastening portion) while securing a sufficient thickness between the vane chamber 80 and the bearing cap without increasing the lateral width of the engine body 1. The fastening rigidity of the central bearing member 54, that is, the actuator AC, to the lower block 41 can be increased.

  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, the structure of the variable stroke link mechanism LV is slightly different from that of the first embodiment.

  The shaft center of the control shaft 65 of the vane hydraulic actuator AC is arranged on the crankshaft 30 side, that is, on the inner side of the crankcase 4 from the pivot connection point by the second connection pin 64 of the lower link 60 and the control link 63. To do. As a result, the engine E is further restrained from increasing the lateral width in the direction orthogonal to the crankshaft 30.

  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.

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 FIG. 6 is a longitudinal sectional view of the vane hydraulic actuator according to the second embodiment of the present invention (corresponding to FIG. 6). FIG. 6 is a longitudinal side view of a part of a variable stroke characteristic engine according to a third embodiment of the present invention.

1 .... Engine body 4 .... Crankcase 11 ... Piston 30 ... Crankshaft 56 ... Transverse fastening member ( Fastening bolt)
65 ········ Control shaft 66 ············································ Cover member (vane bearing)
82 .... Cover member (vane bearing)
83 ・ ・ ・ ・ ・ ・ ・ Crank shaft direction fastening member (fastening bolt)
88... Hydraulic passage 89... Hydraulic passage 73 .. Housing receiving portion 74 .. Fastening member (fastening bolt)
86 ... Vane oil chamber 87 ... Vane E ... Variable stroke characteristics engine AC ... Vane hydraulic actuator LV ... ... Stroke variable link mechanism HU ... Housing LL ... Cylinder axis V-V ... Vertical axis

Claims (4)

The piston (11) and the crankshaft (30) are connected to a control shaft (65) via a variable stroke link mechanism (LV) disposed on the side of the crankshaft (30). 65) is provided on the same axis as the vane type hydraulic actuator (AC), and the hydraulic actuator (AC) drives the control shaft (65) to operate the variable stroke link mechanism (LV) to move the piston (11). A vane type hydraulic actuator mounting structure in a variable stroke characteristic engine with variable stroke,
The vane hydraulic actuator (AC) includes a housing (HU) and a control shaft (65) rotatably provided in the housing (HU), and a vane shaft (66) having a vane (87) protruding from an outer peripheral surface. And a pair of vane oil chambers (86) in which the vanes (87) are accommodated between the housing (HU) and the vane shaft (66),
The housing (HU) is provided in the crankcase (4), is fixed to the crankcase (4), and supports both the crankshaft (30) and the control shaft (65), and The vane oil chamber (86) is arranged side by side in the cylinder axis (LL) direction of the engine body (1) of the variable stroke characteristic engine (E), and the housing (HU) and the crankcase (4) The both sides are fastened by a plurality of lateral fastening members (56) from a direction orthogonal to the cylinder axis (LL) of the engine body (1), and at least a part of the fastening members (56) is a cylinder. characterized in that the axis (L-L) disposed in a direction a pair of vane oil chamber between (86) are provided, a vane type hydraulic activator at the stroke characteristic variable engine Mounting structure of the mediator. The housing (HU) of the actuator (AC) and the cover members (81, 82) covering the opening of the housing (HU) are formed by a plurality of crankshaft direction fastening members (83) extending in the crankshaft (30) direction. The vane hydraulic pressure in the variable stroke characteristic engine according to claim 1 , wherein a part of these crankshaft direction fastening members (83) is fastened and provided between the lateral direction fastening members (56). Actuator mounting structure. Hydraulic passages (88, 89) for supplying hydraulic oil to the pair of vane oil chambers (86) are provided in the housing (HU) while being shifted in the direction of the lateral fastening member (56) and the crankshaft (30). The mounting structure of the vane type hydraulic actuator in the variable stroke characteristic engine according to claim 2 or 3, wherein The cylinder axis (LL) of the engine body (1) is inclined to one side with respect to the vertical line (V-V), and on the other side, the crankcase is lower than the crankshaft (30). 4. The vane hydraulic actuator mounting structure in a variable stroke characteristic engine according to claim 1, wherein the vane hydraulic actuator (AC) is provided in (4) .

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