WO2011047526A1 - 曲柄圆滑块机构的v型机体及其缸套、缸套组、机械设备 - Google Patents

曲柄圆滑块机构的v型机体及其缸套、缸套组、机械设备 Download PDF

Info

Publication number
WO2011047526A1
WO2011047526A1 PCT/CN2010/001324 CN2010001324W WO2011047526A1 WO 2011047526 A1 WO2011047526 A1 WO 2011047526A1 CN 2010001324 W CN2010001324 W CN 2010001324W WO 2011047526 A1 WO2011047526 A1 WO 2011047526A1
Authority
WO
WIPO (PCT)
Prior art keywords
cylinder
cylinder liner
notch
liner
hole
Prior art date
Application number
PCT/CN2010/001324
Other languages
English (en)
French (fr)
Inventor
黎明
黎正中
谭智民
缪会元
冯德坤
Original Assignee
北京中清能发动机技术有限公司
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 北京中清能发动机技术有限公司 filed Critical 北京中清能发动机技术有限公司
Priority to US13/502,904 priority Critical patent/US8931442B2/en
Priority to ES10824367.6T priority patent/ES2557579T3/es
Priority to BR112012009657-5A priority patent/BR112012009657B1/pt
Priority to JP2012534514A priority patent/JP5718343B2/ja
Priority to EP10824367.6A priority patent/EP2492439B1/en
Publication of WO2011047526A1 publication Critical patent/WO2011047526A1/zh

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/32—Engines characterised by connections between pistons and main shafts and not specific to preceding main groups
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F1/00—Cylinders; Cylinder heads 
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B1/00—Reciprocating-piston machines or engines characterised by number or relative disposition of cylinders or by being built-up from separate cylinder-crankcase elements
    • F01B1/04—Reciprocating-piston machines or engines characterised by number or relative disposition of cylinders or by being built-up from separate cylinder-crankcase elements with cylinders in V-arrangement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B1/00—Reciprocating-piston machines or engines characterised by number or relative disposition of cylinders or by being built-up from separate cylinder-crankcase elements
    • F01B1/06—Reciprocating-piston machines or engines characterised by number or relative disposition of cylinders or by being built-up from separate cylinder-crankcase elements with cylinders in star or fan arrangement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B9/00—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups
    • F01B9/02—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with crankshaft
    • F01B9/023—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with crankshaft of Bourke-type or Scotch yoke
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F7/00—Casings, e.g. crankcases or frames
    • F02F7/0002—Cylinder arrangements
    • F02F7/0012—Crankcases of V-engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F04B35/01—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being mechanical
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J1/00—Pistons; Trunk pistons; Plungers
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/18—Mechanical movements
    • Y10T74/18056—Rotary to or from reciprocating or oscillating
    • Y10T74/18248—Crank and slide

Definitions

  • the invention relates to a crank-slider mechanism, in particular a V-shaped body of a crank-slider mechanism.
  • the present invention also provides a cylinder liner and a cylinder liner set for use in a cylinder of the above V-shaped body.
  • the present invention also provides a mechanical device using the above V-shaped body and its cylinder liner and cylinder liner set. Background technique
  • a reciprocating internal combustion engine needs to convert the reciprocating motion of the piston into a rotational motion of the crankshaft.
  • the above-mentioned conversion process requires the use of a crank-and-rod mechanism. Due to the presence of the links in the crank linkage, the machine is bulky, bulky and cannot be fully balanced.
  • a Chinese patent document CN85100358B discloses a "cranked circular slider reciprocating piston type internal combustion engine”
  • a Chinese patent document CN1067741C discloses a “crank double circular slider reciprocating piston type internal combustion engine”
  • Chinese Patent Document CN1 144880A discloses a "Crank multi-circular slider reciprocating piston internal combustion engine”.
  • the common feature of the above internal combustion engine is that the crank-link mechanism of the internal combustion engine under the general technology has been completely improved, and a circular slider having an eccentric circular hole is used instead of the connecting rod.
  • the eccentric circular slider has a cylindrical shape and is provided with an eccentric circular hole parallel to the axis of the cylinder, the eccentric circular hole for passing through the crank pin of the crankshaft.
  • the piston of the internal combustion engine includes a crown portion at both ends and a guiding portion connecting the two crown portions, wherein the guiding portion is provided with a circular hole, and an inner diameter surface of the circular hole is matched with an outer diameter surface of the circular slider, and the circular slider is disposed at
  • the piston guide is in a circular hole that cooperates with its outer circumference.
  • the function of the piston is significantly different from that of the currently used crank-link mechanism internal combustion engine piston.
  • the piston not only functions to withstand the explosive pressure of the combustible mixture and converts it into a linear motion, but also provides a circular slider receiving hole for the circular slider, and the crankshaft passes through the eccentric hole of the circular slider, therefore,
  • the piston in the crank circular slider mechanism is indirectly opposed by a circular slider mounted in the receiving hole of the circular slider The crankshaft is supported.
  • FIG. 1 is a perspective view of a piston for a crank circular slider mechanism, which is shown in FIG. 4 of the specification of the Chinese patent document CN85100358B.
  • the piston of the crank circular slider mechanism includes a crown 1 and a guiding portion 2 , the crown
  • the part 1 has the same function as the piston head of the conventional internal combustion engine, and the top is called the piston top, which is a part of the combustion chamber;
  • the periphery of the crown is provided with a plurality of piston ring grooves for arranging the gas ring and the oil ring to achieve the sealing of the cylinder.
  • the guiding portion 2 in the lower part of the crown, the guiding portion 2 is disposed, the main portion of the guiding portion 2 is in the form of a thin block, and the two sides of the thin piece can cooperate with the slide rail of the body, which is called a guiding side;
  • a circular hole having an inner diameter and an outer diameter of the circular slider is formed on the center line, and the circular hole is called a circular slider receiving hole.
  • the arrangement of the cylinders and the apparatus using the crank-link mechanism are significantly different.
  • the piston needs to be provided with a circular slider accommodating hole for arranging the circular slider, and the crank pin of the crankshaft is to pass through the eccentric hole of the circular slider, so that the main body of the crankshaft of the crankshaft is required to be mounted on the body. Intersecting with the cylinder of the body that provides the piston track, in the existing crank linkage mechanism, the cylinder and the spindle neck hole do not intersect.
  • the circular sliders in the pistons installed in adjacent cylinders need to be as close as possible to reduce the size of the whole machine, and the cylinder spacing between adjacent cylinders will be the distance between the circular sliders. If there is a great influence, if the distance between the circular sliders is increased, the size of the body will increase, which will affect the compactness of the body. How to solve this problem becomes a difficult point in the design of the crank-slider mechanism.
  • Another problem is that when the body of the above V-shaped structure is used as the body of the internal combustion engine, it is generally required to install a cylinder liner in the cylinder, and how to design the appropriate space under the complicated spatial position relationship between the adjacent cylinder and the spindle neck hole.
  • the cylinder liner is made to conform to the structural requirements of the cylinder, and the requirement of increasing the cylinder spacing of the cylinder is not caused by the addition of the cylinder liner, which is also a problem to be solved.
  • the above-mentioned cylinder liner can be conveniently installed in the cylinder, and mutual interference does not occur between adjacent cylinder liners, resulting in assembly difficulties.
  • crank-type slider mechanism in which the V-shaped structure is mounted generally adopts a single-acting piston, that is, a single-acting piston, that is, a piston provided with a crown on one side as shown in FIG. 1; however, in special cases
  • the V-shaped mechanism body is also used for installing a crank circular slider mechanism using a double-acting piston, that is, a double-acting piston, that is, a piston having a crown at both ends of the piston, which is a unique piston form of the crank circular slider mechanism. .
  • the present invention provides a V-shaped body for a crank-slider mechanism that satisfies the special requirements of the crank-slider mechanism for the cylinder, so that the cylinder can provide sufficient reciprocating length for the piston.
  • a compact cylinder design is provided, and the structure of the crank circular slider mechanism using the V-shaped body can be very compact.
  • the invention also provides a cylinder liner which is suitable for the structural requirements of the V-shaped body described above, and the preferred manner of which is more convenient to install.
  • the present invention provides a V-shaped body for a crank circular slider mechanism.
  • the crank circular slider mechanism includes a piston having a circular slider accommodating hole and a circular slider housed in the circular slider accommodating hole.
  • the body has a spindle neck bore and includes a set of adjacent cylinders disposed in a V-shape at a position of the spindle neck bore, each cylinder of the set of adjacent cylinders extending through the spindle bore, respectively.
  • the axial length of the cylinder extending through the neck bore of the main shaft is sufficient to accommodate the reciprocating range of motion of the piston below the portion of the circular slider receiving bore.
  • an inner edge is provided at the bottom opening of the cylinder.
  • the adjacent cylinders are partially overlapped at the intersection, and the wrong cylinder gap is such that the intersection is sufficient to arrange two adjacent circular sliders.
  • the present invention also provides a cylinder liner for the V-shaped body according to any one of the above aspects, wherein the cylinder liner is a thin-walled cylinder having an axial length sufficient to accommodate the reciprocation of the entire piston of the crank-slider mechanism.
  • the cylinder sleeve has a through hole perpendicularly intersecting the central axis of the thin-walled cylinder; after the cylinder is fitted into the cylinder, the through hole is located in the axial direction of the cylinder sleeve so that it is exactly opposite to the spindle
  • the through hole is opposite to the crank pin, which is called a crankshaft through hole; a side wall of the cylinder sleeve is cut off to form a avoidance notch; the position of the avoidance notch meets the following requirements: the crankshaft through hole One of the two truncated circles intersecting the cylinder liner is intercepted by the avoidance notch, and the other truncation is directly facing the avoidance notch; on the axial section of the cylinder liner where the avoidance notch is located, the cylinder liner is avoided by the notch and After the truncation is taken, the width left on both sides is sufficient to provide a guide surface for the piston guide mounted in the cylinder liner
  • the avoidance notch is a recessed portion in the axial middle portion of the cylinder liner, and does not reach the end of the cylinder liner.
  • the position of the avoidance notch in the axial direction of the cylinder sleeve divides the cylinder sleeve into three segments in the axial direction; the first segment is from the first end face of the cylinder liner to the plane of the first side of the avoidance notch,
  • the length of the cylinder sleeve satisfies the length required for the axial movement of the crown of the piston;
  • the second section is the axial extent covered by the avoidance notch;
  • the third section is the plane of the second side of the avoidance notch to the other end of the cylinder liner Axial range; a portion of the third section of the cylinder sleeve is divided into independent arcuate ring portions, and the specific dividing position starts from the boundary line between the second side of the avoidance notch and the bottom edge of the avoidance notch to avoid the bottom of the notch
  • the natural extension of the edge is split.
  • the position of the avoidance notch in the axial direction of the cylinder sleeve divides the cylinder sleeve into three segments in the axial direction; the first segment is from the first end face of the cylinder liner to the plane of the first side of the avoidance notch,
  • the length of the cylinder sleeve satisfies the length required for the axial movement of the crown of the piston;
  • the second section is the axial extent covered by the avoidance notch;
  • the third section is the plane of the second side of the avoidance notch to the other end of the cylinder liner Axial range; a portion of the third section of the cylinder sleeve is divided into independent arcuate ring portions, and the specific dividing position starts from the boundary line between the second side of the avoidance notch and the bottom edge of the avoidance notch, to the cylinder liner
  • the oblique direction of the central axis extends to the bottom end face of the cylinder liner.
  • the invention also provides a cylinder liner set, the cylinder liner set includes two cylinder liners, wherein the first cylinder liner is a cylinder liner that is not divided in the third segment; the second cylinder liner is separated by a third segment a cylinder liner; when assembled, first loading the first cylinder liner and escaping the notch toward the mounting position of the second cylinder liner; and then installing the separated arcuate portion of the second cylinder liner in position, Then, the main part of the second cylinder sleeve is loaded; after installation, the bottom edges of the two cylinder sleeves are close to each other.
  • the present invention also provides a mechanical apparatus which employs the V-shaped body for a crank circular slider mechanism provided by the above technical solution; the mechanical apparatus is specifically an internal combustion engine or a compressor. A set of red sets of cylinders.
  • the V-shaped body for the crank circular slider mechanism provided by the present invention is provided with an extension portion of the cylinder at a lower portion of the main body neck hole of the body to accommodate the piston below the circular slider receiving hole Points, and provides a reciprocating orbit for this part.
  • the structure satisfies the requirements of the piston of the crank-slider mechanism for the moving track, and the total axial length and the length of each segment are sufficient to meet the track length requirements of the reciprocating motion of the piston.
  • the adjacent two cylinders overlap at the intersection portion, and the overlapping portion of the cavity is sufficient to accommodate the two circular sliders in close proximity to each other.
  • the arrangement of the adjacent cylinders overlaps, so that a small misalignment gap can be used between adjacent cylinders, which can effectively reduce the volume of the crank-slider mechanism and the body, and reduce the raw materials consumed in manufacturing the engine.
  • the cylinder liner provided by the invention is provided with a crankshaft passage hole and a avoidance notch. These structures enable the cylinder liner to adapt to the complicated positional relationship between the adjacent cylinders of the V-shaped body and the spindle neck hole, and fit snugly into the cylinder. in.
  • a cylinder liner divided into two parts which can make the cylinder liner which has been installed in an adjacent cylinder when the cylinder is dropped into the cylinder, so as to be installed in the cylinder liner One of the adjacent cylinders can be easily installed.
  • FIG. 1 is a perspective view of a piston of a crank circular slider mechanism disclosed in the prior art
  • Figure 2 is a perspective view of a V-shaped body according to a first embodiment of the present invention
  • Figure 3 is a perspective view of a V-shaped body according to a first embodiment of the present invention
  • Figure 4 is a V of the first embodiment of the present invention. The third perspective of the body;
  • Figure 5 is a perspective view of a cylinder liner according to a second embodiment of the present invention.
  • Figure 6 is a perspective view of another cylinder liner according to a third embodiment of the present invention. detailed description
  • An embodiment of the present application provides a V-shaped body for a crank circular slider mechanism.
  • the V-shaped body is used to mount a crank circular slider mechanism using a single-acting piston.
  • FIG. 2 is a perspective view of a V-shaped body I according to a first embodiment of the present application.
  • the angle of view is the side lower portion of the side of the rear end face of the flywheel housing of the body I.
  • FIG. 3 is a side view of the front end side of the V-shaped body in which the gear chamber cover is mounted.
  • FIG. 4 at the same time, which is a bottom view of the front end side of the V-shaped body mounted gear housing cover.
  • the body I is a two-cylinder V-shaped body, including two V-shaped bodies.
  • the arranged cylinders are respectively a first cylinder 1 1 and a second cylinder 12; the above two cylinders are adjacent and intersect each other.
  • the intersection position is exactly at the position of the spindle neck hole 13.
  • the spindle neck hole 13 is perpendicular to the axis of the first cylinder 11 and the second cylinder 12 through the intersection of the two, the spindle neck hole 13
  • the position passing through the first cylinder 11 and the second cylinder 12 described above is the space in which the circular slider of the crank circular slider mechanism is mounted.
  • the first cylinder 1 1 and the second cylinder 12 continue to extend to the lower portion of the spindle neck hole 13 after the main journal hole 13 intersects, that is, the body portion of the oil pan which is closer to the main shaft neck hole 13 , the axial direction of the extension portion
  • the length is adapted to the axial length of the piston to be loaded into the cylinder below the circular slider seating hole and the length of the reciprocating movement of the piston, and is sufficient to accommodate the circular portion of the piston to accommodate the reciprocating movement of the piston.
  • the circular slider accommodates a portion below the hole, that is, a portion of the piston that is closer to the oil pan side of the body after being installed in the body.
  • An end face of a portion of the first cylinder 1 1 and the second cylinder 12 that extends below the spindle neck hole 13, i.e., the cylinder end, has a bottom end opening that faces the bottom surface of the body on which the oil pan is mounted.
  • An inner edge 14 is provided at the bottom opening.
  • the first cylinder 1 1 and the second cylinder 12 overlap each other at the intersection, that is, the cylinders of the two overlap each other at the intersection, and the wrong cylinder gap of the two adjacent cylinders is smaller than the diameter of any one cylinder, but the error
  • the cylinder gap is of a size sufficient to allow the two cylinders to be interdigitated to accommodate the width of two adjacent circular sliders, i.e., any one of the two circular sliders disposed in the interdigitated space of the cylinders does not extend beyond the cylindrical surface of the cylinder. A boundary that extends in space. After the installation, two adjacent circular sliders are closely adhered to each other in the space in which the cylinders are interlaced, and are integrally fixed.
  • the so-called wrong cylinder gap that is, the distance between the central axes of the two cylinders.
  • the above V-shaped body structure better solves the problem of the V-shaped body arrangement caused by the long cylinder length in the crank-slider mechanism, and the V-shaped body is applied to the crank-circular slider machine. And the advantage of compact structure can be obtained.
  • FIG. 5 a perspective view of a cylinder liner provided by a second embodiment of the present application is shown.
  • the cylinder liner II is a thin-walled cylinder whose axial length is to be loaded The cylinders of the cylinder liner cooperate, the axial length of the cylinder liner is significantly longer than the cylinder liner of the internal combustion engine using the crank linkage mechanism, the length being sufficient to accommodate the reciprocating motion of the entire piston of the crank circular slider mechanism in the axial direction.
  • a collar is arranged on the outer diameter surface of one end of the cylinder liner II.
  • the collar When the cylinder liner II is installed in the cylinder, the collar will be blocked by the end surface of the cylinder end, so that the cylinder sleeve II can be axially positioned.
  • the collar is referred to as a support shoulder 23.
  • the end surface on which the support shoulder 23 is provided is the top end surface of the cylinder liner, and the other end surface opposite thereto is referred to as the bottom end surface of the cylinder liner.
  • a guide chamfer 24 is provided which facilitates insertion of the cylinder liner II into the cylinder.
  • a through hole having an axis perpendicularly intersecting a central axis of the thin-walled cylinder is formed in the cylinder liner II, and the through hole is located in the axial direction of the cylinder liner II so that after the cylinder is fitted into the cylinder, the The main shaft hole 13 is opposed to each other, and the through hole is coaxial with the main journal hole 13 as long as the cylinder liner II is appropriately adjusted in the circumferential direction.
  • the through hole in the cylinder liner II described above is passed through the crank pin of the crankshaft, and is referred to as a crankshaft passage hole 21.
  • a section of the side wall of the cylinder liner II is cut away to form a relief notch 22;
  • the avoidance notch 22 is obtained by taking a plane parallel to the axis of the cylinder liner II and perpendicular to the axis of the crankshaft through the hole 21, the intercepting position and The intercept depth satisfies the following requirements: one of the two truncated circles intersecting the cylinder bore through the hole 21 is intercepted by the avoidance notch 22, and the other truncation is directed to the avoidance notch 22;
  • On the axial section of the cylinder liner II the side wall of the cylinder liner II is prevented from being cut by the notch 22 and cut off, and the width left on both sides thereof is sufficient to provide a guide surface for the piston guide portion installed in the cylinder liner II. .
  • the relief recess 22 is located in the axially intermediate portion of the cylinder liner II and does not reach the end of the cylinder liner. Therefore, the avoidance notch 22 is a U-shaped portion including the first side 22-1, the second side 22-3, and a bottom edge .22-2.
  • the range of the relief recess 22 in the axial direction of the cylinder liner II divides the cylinder liner II into three segments in the axial direction; the first segment is the first end face of the cylinder liner provided with the support shoulder 23 to the first to avoid the gap
  • the plane of the side 22-1, the length of the cylinder liner II meets the length required for the axial movement of the piston crown; the second section is the axial extent covered by the avoidance notch 22; the third section is the avoidance of the notch 22
  • the third segment is relatively short in the axial direction.
  • the avoidance notches 22 of the adjacent cylinder liners II can be brought close to each other or even adhered to the bottom edge 22-2, which is equivalent to the intersection of the two cylinder liners II.
  • the parts provide a gap that is embedded in each other and cooperates with the smaller cylinder misalignment of the cylinder.
  • the cylinder liner provided by the second embodiment described above can perform its function in a static mounting position, but It is not considered how to load into the cylinder.
  • the third section of the cylinder liner is a complete circle, when the first cylinder liner II is loaded into the cylinder, the cylinder liner II installed in the adjacent cylinder needs to be inserted into the cylinder, and the third section thereof It will interfere with the portion of the avoidance notch 22 of the already installed cylinder liner II, so that the cylinder liner II cannot be loaded.
  • the third embodiment of the present invention provides a cylinder liner that cooperates with the cylinder liner II provided in the second embodiment to solve the interference problem in the above installation.
  • the cylinder liner III and the second embodiment are basically the same, but in the third section of the cylinder liner III, that is, the second side 22-3 of the recess 22 is avoided to the support shoulder 23.
  • a separate arcuate cymbal 25 is cut, the dividing position of the arcuate ring 25 starting from the boundary line between the second side 22-3 of the avoidance notch 22 and the bottom edge 22-2 of the avoidance notch 22. , extending to the bottom end surface of the cylinder liner in an oblique direction approaching the central axis of the cylinder liner III.
  • the avoidance notch 22 is directed toward the phase thereof. Adjacent cylinder.
  • the cylinder liner III provided in this embodiment is incorporated in the adjacent cylinder. The specific installation process is to first place the arcuate ring 25 into the bottom end opening of the cylinder bottom to be loaded into the cylinder liner, with the inner edge 14 as the positioning surface of the arcuate ring 25.
  • the main part of the cylinder liner III is inserted into the cylinder, and since the portion of the third section of the cylinder liner III that is higher than the avoidance notch 22 has been cut off, the third section of the cylinder liner III does not interfere with the avoidance notch 22 of the cylinder liner II.
  • the avoidance notch 22 of the cylinder liner III can be smoothly passed close to the avoidance notch 22 of the installed cylinder liner II, and the avoidance notches 22 of the two cylinder sleeves are close to each other or even fit in the final installation position, so that the spacing between the two cylinder liners Reduced, in line with the requirements to reduce the size of the body.
  • the third section is complementary to the already mounted arcuate ring 25 to form a complete jaw.
  • the inclination angle of the boundary line between the curved ring 25 and the main portion of the cylinder III has a guiding effect, so that the installation fit of the two is smoother.
  • the dividing line can also adopt a straight line, that is, directly adopting the natural extension of the bottom edge 22-2 as a dividing line, so that it is obviously troublesome to install, and the position of the curved ring 25 is slightly biased, which makes the cylinder liner It is difficult for the main body to enter the bottom of the cylinder.
  • the cylinder liners provided in the second embodiment and the third embodiment described above are combined in pairs, that is, obtained An embodiment of a cylinder liner set.
  • the body provided by the first embodiment described above is used for an internal combustion engine or a compressor employing a crank-slider mechanism, i.e., an embodiment relating to an internal combustion engine or a compressor is obtained.
  • V-shaped bodies having a pair of V-shaped arrangement cylinders.
  • the V-shaped body may be a V-shaped body having two or more pairs of V-shaped cylinders, for example, A plurality of pairs of V-shaped cylinders are sequentially arranged along the extending direction of the crankshaft axis.
  • two or more pairs of V-type cylinders may be arranged using other prior art or techniques that may be developed in the future, which cylinders are also within the general scope of the above embodiments.
  • the pistons mounted in the V-shaped cylinder are assumed to be single-acting pistons in the above embodiment, the above-described cylinder structure is also applicable to a cylinder employing a double-acting piston, and the structure thereof is the same as that of the above embodiment.
  • the axial length of the cylinder extending to the lower part of the spindle neck hole needs to be set according to the needs of setting the combustion chamber, for example, referring to the cylinder portion at the upper part of the spindle neck hole; at this time, the cylinder portion at the lower part of the spindle neck hole also needs to be burned. Part of the room is designed.

Description

曲柄圆滑块机构的 V型机体及其缸套、 缸套组、 机械设备 技术领域
本发明涉及曲柄圆滑块机构，特别是曲柄圆滑块机构的 V型机体。 本发明同时提供用于上述 V型机体的气缸中的缸套以及缸套组。 本发 明同时提供一种采用上述 V型机体及其缸套、 缸套组的机械设备。 背景技术
往复式内燃机需要将活塞的往复运动转换为曲轴的旋转运动。 目 前的通用技术下， 上述转换过程均需要使用曲柄连杆机构。 由于曲柄 连杆机构中连杆的存在， 使机器庞大、 笨重， 无法完全平衡。
为了解决上述问题， 中国专利文献 CN85100358B公开了一种 "曲 柄圆滑块往复活塞式内燃机"， 中国专利文献 CN1067741C公开了一种 "曲柄双圆滑块往复活塞式内燃机" , 中国专利文献 CN1 144880A 公 开了一种 "曲柄多圆滑块往复活塞式内燃机" 。 上述内燃机的共同特 点是对通用技术下内燃机的曲柄连杆机构进行了彻底改进， 采用具有 偏心圆孔的圆滑块代替连杆。 所述偏心圆滑块呈圆柱形， 并且开有平 行于圆柱体轴线的偏心圆孔， 该偏心圆孔用于穿过曲轴的曲柄销。 该 内燃机的活塞包括两端的冠部和连接两冠部的导向部， 其中导向部上 开有圆孔， 该圆孔的内径面和上述圆滑块的外径面相配合， 所述圆滑 块即安置在活塞导向部上与其外周相配合的圆孔中。 当所述活塞受到 气缸中燃烧气体的推动而在气缸中往复运动时， 所述偏心圆滑块绕其 自身的圆心转动， 并进而带动曲轴反向转动， 从而将活塞的往复运动 转化为曲轴的旋转运动， 再通过与曲轴连接的旋转部件向外传递功率。 上述专利的思想也可以方便的转用到压缩机或者抽真空机中， 获得曲 柄圆滑块压缩机或者曲柄圆滑块抽真空机。
上述专利提供的曲柄圆滑块机构中， 其活塞的功能较目前广泛使 用的曲柄连杆机构内燃机活塞有明显的差异。 在该机构中， 活塞不仅 起到承受可燃混合气的爆发压力并将其转化为直线运动的作用， 还为 圆滑块提供圆滑块容置孔， 而曲轴又穿过圆滑块的偏心孔， 因此， 曲 柄圆滑块机构中的活塞通过安装在其圆滑块容置孔中的圆滑块间接对 曲轴进行支撑。
为适应活塞的功能变化， 曲柄圆滑块机构的活塞结构也做了相应 的改变。 请参看图 1， 该图为中国专利文献 CN85100358B说明书图 4 绘制的用于曲柄圆滑块机构的活塞立体图， 如图所示， 曲柄圆滑块机 构的活塞包括冠部 1和导向部 2 ,所述冠部 1与传统内燃机的活塞头作 用相同， 其顶部称为活塞顶， 为燃烧室的一部分； 冠部周边则设置有 若干活塞环槽， 用于安置气环、 油环， 实现对气缸的密封。 图中， 在 冠部下部， 设置所述导向部 2， 该导向部 2主体部分为薄块状， 该薄块 的两个侧边能够与机体的滑道配合， 称为导向側面； 其平面的中心线 上则开有内径和圆滑块外径配合的圆孔， 该圆孔称为圆滑块容置孔。
与上述活塞结构的变化相适应， 采用曲柄圆滑块机构的设备中， 其气缸的设置和采用曲柄连杆机构的设备有明显区别。 采用曲柄圆滑 块机构的设备的机体中， 活塞需设置有安置圆滑块的圆滑块容置孔， 并且曲轴的曲柄销要穿过圆滑块的偏心孔， 使机体上为安装曲轴的主 轴颈孔需要与提供活塞轨道的机体气缸相交， 而现有的曲柄连杵机构 中， 气缸与主轴颈孔不会相交。 因此， 在采用曲柄圆滑块机构的情况 下， 如何布置气缸， 使主轴颈孔横穿气缸的结构下， 仍然能够为活塞 提供足够其往复运动的气缸轴向长度， 成为一个有待解决的问题。 尤 其是在采用 V型结构的机体时， 相邻气缸呈 V型布置， 而曲柄圆滑块 机构的气缸较长， 加之各个气缸需要和主轴颈孔交叉， 机体空间布置 更加复杂。 现有技术中， 没有提供解决上述问题的技术方案。
在使用 V型结构的机体时， 相邻气缸中安装的活塞中的圆滑块需 要尽量贴近以达到减小整机尺寸的目的， 而相邻气缸之间的缸间距会 对圆滑块之间的距离有很大影响， 圓滑块距离若增大， 则机体尺寸必 然增加， 影响机体的紧凑性。 如何解决这一问题成为曲柄圆滑块机构 的机体设计的一个难点。
另一个问题是，在使用上述 V型结构的机体作为内燃机的机体时， 一般需要在气缸中装入缸套， 在相邻气缸以及主轴颈孔之间的复杂的 空间位置关系下， 如何设计合适的缸套， 使其符合气缸的结构要求， 并且不因为增加了缸套而产生增加气缸的缸间距的要求， 同样是一个 有待解决的问题。 另外， 还需要上述缸套能够方便的装入气缸中， 相 邻缸套之间不会产生相互干涉， 造成装配困难。 上述采用 V型结构的机体， 安装在其中的曲柄圆滑块机构一般采 用单作用活塞， 所谓单作用活塞， 即如图 1 所示的只有一側设置有冠 部的活塞； 但是， 在特殊情况下， 这种 V型机构机体也用于安装采用 双作用活塞的曲柄圓滑块机构， 所谓双作用活塞， 即活塞的两端都设 置有冠部的活塞， 是曲柄圆滑块机构独有的活塞形式。
发明内容
针对上述问题， 本发明提供用于曲柄圆滑块机构的 V型机体， 该 V 型机体满足了曲柄圆滑块机构对气缸的特殊要求， 使该气缸能够为 活塞提供足够的往复运动长度。
本发明的进一步优选方案中， 提供了结构紧凑的气缸设计形式， 采用该 V型机体的曲柄圆滑块机构的结构能够非常紧凑。
本发明还提供一种缸套， 该缸套适合上述 V型机体的结构要求， 其优选方式更能够方便的进行安装。
本发明提供了用于曲柄圓滑块机构的 V型机体。 该曲柄圆滑块机 构包括具有圆滑块容置孔的活塞和容置在圓滑块容置孔内的圓滑块。 所述机体具有主轴颈孔并包括在主轴颈孔位置交叉的呈 V型设置的一 组相邻气缸， 该组相邻气缸中的每个气缸分别穿过主轴颈孔延伸， 其 中每个所述气缸穿过主轴颈孔之后延伸的轴向长度足够容纳活塞位于 其圆滑块容置孔以下部分的往复运动的活动范围。
优选的， 在所述气缸的底部开口处设置有内沿。
优选的， 所迷相邻气缸在交叉部位部分叠合， 其错缸间隙使该交 叉部位足以布置两个相邻的圆滑块。
本发明还提供一种缸套， 用于上述各技术方案任一项所述的 V型 机体， 该缸套为一个薄壁筒体， 其轴向长度足以容纳曲柄圆滑块机构 的整个活塞的往复运动； 该缸套上开有轴线与薄壁筒体的中心轴线垂 直相交的通孔， 在该缸套装入气缸后， 该通孔在缸套轴向上的位置， 使其恰好与所述主轴颈孔相对， 该通孔供曲轴曲柄销穿过， 称为曲轴 通过孔； 所述缸套的一段側壁被截去， 形成避让缺口； 该避让缺口所 在位置满足下述要求： 所述曲轴通过孔与缸套相交的两个截圆中的一 个被该避让缺口截去， 另一个截圆正对该避让缺口； 在该避让缺口所 在的缸套轴向段上， 所述缸套被避让缺口和截圆截取后， 其两側留下 的宽度足以为安装在该缸套中的活塞导向部提供导轨面。 优选的， 所述避让缺口采用平行于缸套轴线并垂直于所述曲轴通 过孔轴线的平面截取获得。
优选的， 所述避让缺口为缸套轴向中部的凹陷部位， 未达到缸套 的端头。
优选的， 所述避让缺口在缸套轴向上的位置范围使缸套在轴向上 分成三段； 第一段从缸套的第一端面到避让缺口的第一側边所在平面， 这段缸套的长度满足活塞冠部轴向运动所需要的长度； 第二段为避让 缺口所覆盖的轴向范围； 第三段为避让缺口的第二侧边所在平面到缸 套的另一端面的轴向范围； 所述缸套轴向上的第三段一部分被分割成 为独立的弧形圈部分， 具体分割位置从避让缺口第二侧边与避让缺口 底边的交界线开始， 以避让缺口底边的自然延伸线进行分割。
优选的， 所述避让缺口在缸套轴向上的位置范围使缸套在轴向上 分成三段； 第一段从缸套的第一端面到避让缺口的第一侧边所在平面， 这段缸套的长度满足活塞冠部轴向运动所需要的长度； 第二段为避让 缺口所覆盖的轴向范围； 第三段为避让缺口的第二側边所在平面到缸 套的另一端面的轴向范围； 所述缸套轴向上的第三段一部分被分割成 为独立的弧形圈部分， 具体分割位置从避让缺口第二侧边与避让缺口 底边的交界线开始， 以向缸套中轴线接近的倾斜方向延伸到缸套底部 端面。
本发明同时提供一种缸套组， 该缸套组包括两个缸套， 其中第一 个缸套为上述第三段没有被分割的缸套； 第二个缸套为第三段被分隔 的缸套； 组装时， 首先装入所述第一个缸套并且其避让缺口朝向第二 个缸套的安装位置； 然后将所述第二个缸套的被分离的弧形圏部分安 装到位， 再将第二缸套的主体部分装入； 安装后， 两个缸套的避让缺 口底边相互贴近。
本发明同时提供一种机械设备， 该机械设备采用上述技术方案提 供的用于曲柄圆滑块机构的 V型机体； 该机械设备具体是内燃机或者 压缩机。 个紅套的缸套组。
本发明提供的用于曲柄圆滑块机构的 V型机体， 在机体的主轴颈 孔的下部设置了气缸的延伸部分， 以容纳活塞在圆滑块容置孔以下部 分， 并为该部分提供往复运动的轨道。 该结构满足了曲柄圆滑块机构 的活塞对运动轨道的要求， 其轴向总长度以及各段长度足以满足活塞 往复运动的轨道长度要求。
在本发明的优选实施方式中， 相邻的两个气缸之间在交叉部位部 分重叠， 重叠部分的空腔足以容纳两个圆滑块彼此贴近设置。 这种相 邻气缸重叠设置的形式， 使相邻气缸之间可以采用较小的错缸间隙， 能够有效减少曲柄圆滑块机构以及机体的体积， 降低制造发动机消耗 的原材料。
本发明提供的缸套， 设置有曲轴通过孔以及避让缺口， 这些结构 使该缸套能够适应 V型机体的相邻气缸和主轴颈孔之间的复杂的位置 关系， 非常贴合的装入气缸中。 在该缸套的优选实施方式中， 还提供 一种分为两个部分的缸套， 这种缸套能够使其落入气缸时， 避让已经 安装在相邻气缸中的缸套， 使安装在相邻气缸中的一个缸套组能够方 便安装。 附图说明
图 1是现有技术公开的曲柄圆滑块机构的活塞立体图；
图 2是本发明第一实施例提供的 V型机体的立体图之一； 图 3是本发明第一实施例提供的 V型机体的立体图之二； 图 4是本发明第一实施例提供的 V型机体的立体图之三；
. 图 5是本发明第二实施例提供的一种缸套的立体图；
图 6是本发明第三实施例提供的另一种缸套的立体图。 具体实施方式
本申请笫一实施例提供一种用于曲柄圆滑块机构的 V型机体。 该 V型机体用于安装采用单作用活塞的曲柄圆滑块机构。
请参看图 2，该图为本申请第一实施例提供的 V型机体 I的立体图。 其视角为该机体 I的安装飞轮壳的后端面一側的侧下部。请同时参看图 3 , 该图视角为该 V型机体安装齿轮室盖的前端面一侧的侧视图。 请同 时参看图 4， 该图视角为该 V型机体安装齿轮室盖的前端面一側的仰 视图。
如图所示， 该机体 I为双气缸的 V型机体， 包括两个相互呈 V型 布置的气缸， 分别为第一气缸 1 1、 第二气缸 12; 上述两个气缸相邻并 且相互交叉。 交叉位置正好在主轴颈孔 13的位置， 从图 4可以看出， 该主轴颈孔 13垂直所述第一气缸 1 1和第二气缸 12的轴线穿过两者的 交叉部位， 主轴颈孔 13穿越上述第一汽缸 1 1和第二气缸 12的位置就 是安装曲柄圓滑块机构的圆滑块的空间。 上述笫一气缸 1 1和第二气缸 12在主轴颈孔 13交叉后继续延伸到所述主轴颈孔 13下部， 即相对主 轴颈孔 13更靠近油底壳的机体部分， 该延伸部分的轴向长度与待装入 上述气缸的活塞在圆滑块安置孔以下部分的轴向长度以及活塞往复运 动的长度相适应， 并足够容纳活塞的圆滑块容置孔以下部分随活塞整 体往返运动。 所述圆滑块容置孔以下部分， 也就是安装入机体后， 活 塞的更靠近机体的油底壳一側的部分。
所述第一气缸 1 1和第二气缸 12的延伸到主轴颈孔 13以下的部分 的端面， 即该气缸末端， 具有底端开口， 该开口朝向安装油底壳的机 体底面。 在该底端开口处设置有内沿 14。
上述第一气缸 1 1 和第二气缸 12在交叉部位相互叠合， 即两者的 圆柱体在交叉部位相互重合， 上述两个相邻气缸的错缸间隙小于任意 一个气缸的直径， 但是该错缸间隙的大小足以使该两个气缸相互交错 的部位能够容纳两个相邻圆滑块的宽度， 即在气缸相互交错的空间安 置的两个圆滑块的任何一个部分不会超出气缸的圆柱面在空间上延伸 的边界。 安装完毕后， 两个相邻圆滑块在该气缸相互交错的空间中相 互贴紧， 固为一体。 所谓错缸间隙， 即两个气缸的中心轴线之间的距 离。
上述 V型机体结构较好的解决了曲柄圆滑块机构中， 由于气缸长 度较长而造成的 V型机体布置难题， 使 V型机体应用于曲柄圆滑块机 构成为可能。 并且可获得结构紧凑的优点。
在将上述 V型机构用于内燃机后， 气缸中一般还需要装入缸套。 这种结构对于缸套的装入显然造成了很多困难。 由于两个相邻气缸具 有叠合部位， 则第一个气缸中装入缸套后， 第二个气缸的缸套将被第 一个气缸中装入的缸套挡住， 无法下入底部。 为此， 需要设计特殊的 缸套。
请参看图 5， 该图示出本申请第二实施例提供的一种缸套的立体 图。 如图 5所示， 该缸套 II为一个薄壁筒体， 其轴向长度与待装入该 缸套的气缸相配合， 该缸套 Π的轴向长度比采用曲柄连杆机构内燃机 的缸套明显长许多， 该长度足以容纳曲柄圆滑块机构的整个活塞在轴 向上的往复运动。 在该缸套 II的一端的外径面上， 设置有凸圈， 当缸 套 II装入气缸后， 该凸圈将被气缸顶端端面挡住， 这样就可以为缸套 II提供轴向定位， 因此， 该凸圈称为支撑肩 23。 该设置了支撑肩 23的 端面为缸套的顶部端面， 与其相对的另一端面称为缸套的底部端面。 在薄壁筒体侧壁与缸套 II 的底部端面相交接的棱部位置， 设置有导向 倒角 24, 该导向倒角 24使该缸套 II便于插入气缸。
在该缸套 II上开有轴线与薄壁筒体的中心轴线垂直相交的通孔， 该通孔在缸套 II轴向上的位置， 使其在该缸套装入气缸后， 恰好与所 述主轴颈孔 13相对， 只要在周向上对该缸套 II适当调节即可使该通孔 与主轴颈孔 13同轴。 上述缸套 II上的通孔供曲轴曲柄销穿过， 称为曲 轴通过孔 21。 所述缸套 II的一段侧壁被截去， 形成避让缺口 22; 所述 避让缺口 22采用平行于缸套 II的轴线并垂直于所述曲轴通过孔 21轴 线的平面截取获得， 其截取位置和截取深度满足下述要求： 所述曲轴 通过孔 21 与缸套相交的两个截圆中的一个被该避让缺口 22截去， 另 一个截圆正对该避让缺口 22; 在该避让缺口 22所在的缸套 II轴向段 上， 所述缸套 II侧壁被避让缺口 22和截圆截去后， 其两侧留下的宽度 足以为安装在该缸套中 II的活塞导向部提供导轨面。
所述避让缺口 22位于缸套 II的轴向中间部位，未达到缸套的端头。 因此， 该避让缺口 22为包括第一侧边 22-1、 第二侧边 22-3 两个侧边 和一个底边.22-2的 U形部位。 所述避让缺口 22在缸套 II轴向上的位 置范围使缸套 II在轴向上分成三段； 第一段是从缸套的设置有支撑肩 23的第一端面到避让缺口的第一侧边 22-1所在平面，这段缸套 II的长 度满足活塞冠部轴向运动所需要的长度； 第二段为避让缺口 22所覆盖 的轴向范围；第三段为避让缺口 22的第二侧边 22-3所在平面到缸套的 另一端面的轴向范围。 其中第三段在轴向上比较短。
上述实施例提供的缸套 II用于上述 V形机体时， 可以使相邻缸套 II的避让缺口 22相互以底边 22-2贴近甚至贴合，相当于为两个缸套 II 的相交叉部位提供了相互嵌入的缺口， 与气缸较小的错缸间隙配合。 当两个此种缸套 II配合使用时， 即获得了一个缸套组。
上述第二实施例提供的缸套在静态安装位置可以实现其功能， 但 是没有考虑如何装入气缸中。 实际上， 由于所述缸套的第三段为一个 完整的圆形， 当第一个缸套 II装入气缸后， 安装在相邻气缸中的缸套 II需要插入气缸时， 其第三段会和已经安装好的缸套 II的避让缺口 22 部分发生干涉， 使该缸套 II无法装入。 上述安装问题可以在机体 I的 设计上予以解决，即在相应部位设置可拆卸的盖体作为机体 I的组成部 分， 将后装的缸套 II装入后再将该盖体装上， 这样就可以使用上述第 二实施例提供的缸套组。 显然， 这种解决方案大幅提高了机体的设计 和制造难度， 并非合理的解决方案。
本申请第三实施例提供一种缸套， 该缸套与上述第二实施例提供 的缸套 II配合， 能够很好的解决上述安装中的干涉问题。
请参看图 6， 该图提供的缸套 III和笫二实施例基本相同， 但是， 在该缸套 III的第三段， 即避让缺口 22第二側边 22-3到未设置支撑肩 23 的端面这一段上， 被切出一个分离的弧形圏 25， 该弧形圈 25 的分 割位置从避让缺口 22的第二侧边 22-3与避让缺口 22的底边 22-2的交 界线开始， 以向缸套 III中轴线接近的倾斜方向延伸到缸套底部端面。 由于所述弧形圏 25与缸套 III整体可以分离， 因此， 在 V形机中， 首 先将一个上述第二实施例提供的缸套 II装入一个气缸后， 将其避让缺 口 22朝向其相邻的气缸。 该相邻气缸中装入本实施例提供的缸套 III。 具体安装过程是， 将弧形圈 25首先装入待装入缸套的气缸底部底端开 口处， 以内沿 14作为该弧形圈 25的定位面。 然后， 将缸套 III的主体 部分插入该气缸， 由于缸套 III第三段的高于避让缺口 22的部分已经 被切除， 使缸套 III第三段不会与缸套 II的避让缺口 22干涉， 该缸套 III的避让缺口 22可以顺利贴近已经安装的缸套 II的避让缺口 22并通 过， 两个缸套的避让缺口 22在最终安装位置相互贴近甚至贴合， 使两 个缸套的间距缩小， 符合减小机体尺寸的要求。 缸套 III插入气缸后， 在气缸底部，其第三段与已经装入的弧形圈 25互补，形成完整的釭套。 弧形圈 25和气缸 III主体部分的分界线的倾斜角度， 具有导向作用， 使两者的安装配合更为顺畅。 实际上， 该分界线也可以采用直线， 即 直接采用底边 22-2的自然延伸作为分界线， 这样安装时显然会比较麻 烦， 弧形圈 25安装的位置稍微偏一点， 就会使缸套 III主体难以下入 气缸底部。
上述第二实施例和第三实施例提供的缸套相互成对组合， 即获得 缸套组的实施例。
将上述第一实施例提供的机体用于采用曲柄圆滑块机构的内燃机 或者压缩机， 即获得有关内燃机或者压缩机的实施例。
本申请的上述实施例均为具有一对 V型布置气缸的 V型机体， 实 际上， 所述的 V型机体可以为具有两对或者多对 V型布置的气缸的 V 型机体， 例如， 可以沿曲轴轴线延伸方向依次布置多对 V型气缸。 当 然， 也可以采用其它现有技术或者未来可能发展的技术布置两对或两 对以上的的 V型气缸， 这些气缸也在上述实施例的概括范围内。
尽管上述实施例中， 安装在所述的 V 型气缸中的活塞均假定为单 作用活塞， 但是， 上述气缸结构也同样适用于采用双作用活塞的气缸， 此时， 其结构和上述实施例相一致， 但气缸延伸到主轴颈孔下部的轴 向长度则需要按照设置燃烧室的需要设置， 例如参考主轴颈孔上部的 气缸部分设置； 此时， 在主轴颈孔下部的气缸部分也需要作为燃烧室 的一部分进行设计。
以上所述仅是本发明的优选实施方式， 应当指出， 对于本技术领 域的普通技术人员来说， 在不脱离本发明基本原理的前提下， 还可以 做出若干改进和润饰， 这些改进和润饰也应视为本发明的保护范围。

Claims

权 利 要 求
1. 一种用于曲柄圆滑块机构的 V型机体， 该曲柄圆滑块机构包括 具有圆滑块容置孔的活塞和容置在圓滑块容置孔内的圆滑块， 所述机 体具有主轴颈孔并包括在主轴颈孔位置交叉的呈 V型设置的一组相邻 气缸， 该组相邻气缸中的每个气缸分别穿过主轴颈孔延伸， 其中每个 所述气缸穿过主轴颈孔之后延伸的轴向长度足够容納活塞位于其圆滑 块容置孔以下部分的往复运动所需的活动范围。
2. 根据权利要求 1所述的曲柄圆滑块机构的 V型机体， 其特征在 于， 在所述气缸的底部开口处设置有内沿。
3. 根据权利要求 1所述的曲柄圆滑块机构的 V型机体， 其特征在 于， 所述相邻气缸在交叉部位部分叠合， 其错缸间隙使该交叉部位足 以布置两个相邻的圆滑块。
4. 一种缸套，用于权利要求 1 - 3任一项所述的用于曲柄圆滑块机 构的 V型机体， 其特征在于， 该缸套为一个薄壁筒体， 其轴向长度足 以容纳曲柄圆滑块机构的整个活塞的往复运动； 该缸套上开有轴线与 薄壁筒体的中心轴线垂直相交的通孔， 在该缸套装入气缸后， 该通孔 在缸套轴向上的位置， 使其恰好与所述主轴颈孔相对， 该通孔供曲轴 曲柄销穿过， 称为曲轴通过孔； 所述缸套的一段侧壁被截去， 形成避 让缺口； 该避让缺口所在位置满足下述要求： 所述曲轴通过孔与缸套 相交的两个截圆中的一个被该避让缺口截去， 另一个截圆正对该避让 缺口； 在该避让缺口所在的缸套轴向段上， 所述缸套被避让缺口和截 圆截取后， 其两侧留下的宽度足以为安装在该缸套中的活塞导向部提 供导轨面。
5. 根据权利要求 4所述的缸套， 其特征在于， 所述避 l:缺口采用 平行于缸套轴线并垂直于所述曲轴通过孔轴线的平面截取获得。
6. 据权利要求 5所述的缸套， 其特征在于， 所述避让缺口为缸 套轴向中部的 陷部位， 未达到缸套的端头。
7. 根据权利要求 6所述的缸套， 其特征在于， 所述避让缺口在缸 套轴向上的位置范围使缸套在轴向上分成三段； 第一段从缸套的第一 端面到避让缺口的第一侧边所在平面， 这段缸套的长度满足活塞冠部 轴向运动所需要的长度； 第二段为避让缺口所覆盖的轴向范围； 第三 段为避让缺口的第二侧边所在平面到缸套的另一端面的轴向范围； 所 述缸套轴向上的第三段一部分被分割成为独立的弧形圈部分， 具体分 割位置从避让缺口第二侧边与避让缺口底边的交界线开始 , 以避让缺 口底边的自然延伸线进行分割。
8. 根据权利要求 6所述的缸套， 其特征在于， 所述避让缺口在缸 套轴向上的位置范围使缸套在轴向上分成三段； 第一段从缸套的第一 端面到避让缺口的第一侧边所在平面， 这段缸套的长度满足活塞冠部 轴向运动所需要的长度； 第二段为避让缺口所覆盖的轴向范围； 第三 段为避让缺口的第二侧边所在平面到缸套的另一端面的轴向范围； 所 述缸套轴向上的第三段一部分被分割成为独立的弧形圏部分， 具体分 割位置从避让缺口第二側边与避让缺口底边的交界线开始， 以向缸套 中轴线接近的倾斜方向延伸到缸套底部端面。
9. 一种缸套组， 包括两个缸套， 其特征在于， 其中第一个缸套为 权利要求 4-6任意一项所述的缸套， 并且其第三段没有被分割； 第二个 缸套为权利要求 7或者权利要求 8所述的缸套； 组装时， 首先装入所 述第一个缸套并且其避让缺口朝向第二个缸套的安装位置； 然后将所 述第二个缸套的被分离的弧形圈部分安装到位， 再将第二缸套的主体 部分装入； 安装后， 两个缸套的避让缺口底边相互贴近。
10. 一种机械设备， 其特征在于， 釆用所述权利要求 1 -3任意一项 所述的用于曲柄圆滑块机构的 V型机体； 该机械设备具体是内燃机或 者压缩机。
1 1. 根据权利要求 10所述的机械设备， 其特征在于， 该机械设备 的气缸中安装有权利要求 9所述的缸套组。
PCT/CN2010/001324 2009-10-22 2010-08-31 曲柄圆滑块机构的v型机体及其缸套、缸套组、机械设备 WO2011047526A1 (zh)

Priority Applications (5)

Application Number Priority Date Filing Date Title
US13/502,904 US8931442B2 (en) 2009-10-22 2010-08-31 V-type block of a crank circular slider mechanism and a cylinder liner, a group of the cylinder liner, mechanical equipment thereof
ES10824367.6T ES2557579T3 (es) 2009-10-22 2010-08-31 Cuerpo de máquina en forma de V para mecanismo de bloque corredero circular de manivela, camisas de cilindro, grupo de camisas de cilindro y dispositivo mecánico
BR112012009657-5A BR112012009657B1 (pt) 2009-10-22 2010-08-31 camisa de cilindro usada em um bloco tipo v, grupo de camisa de cilindro e equipamento mecânico
JP2012534514A JP5718343B2 (ja) 2009-10-22 2010-08-31 シリンダスリーブ及び機械的デバイス
EP10824367.6A EP2492439B1 (en) 2009-10-22 2010-08-31 V-shape machine body for crank round sliding block mechanism, cylinder sleeves, cylinder sleeve group and mechanical device

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN200910236200.6 2009-10-22
CN2009102362006A CN101761359B (zh) 2009-10-22 2009-10-22 一种v型机体及其缸套、缸套组、内燃机、压缩机

Publications (1)

Publication Number Publication Date
WO2011047526A1 true WO2011047526A1 (zh) 2011-04-28

Family

ID=42492728

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2010/001324 WO2011047526A1 (zh) 2009-10-22 2010-08-31 曲柄圆滑块机构的v型机体及其缸套、缸套组、机械设备

Country Status (7)

Country Link
US (1) US8931442B2 (zh)
EP (1) EP2492439B1 (zh)
JP (1) JP5718343B2 (zh)
CN (1) CN101761359B (zh)
BR (1) BR112012009657B1 (zh)
ES (1) ES2557579T3 (zh)
WO (1) WO2011047526A1 (zh)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101761359B (zh) * 2009-10-22 2012-05-09 北京中清能发动机技术有限公司 一种v型机体及其缸套、缸套组、内燃机、压缩机
CN101886693B (zh) 2010-07-02 2014-02-12 北京中清能发动机技术有限公司 一种曲柄圆滑块机构及设备
CN102072037B (zh) * 2010-12-06 2012-08-22 北京中清能发动机技术有限公司 一种机体以及应用该机体的压缩机、内燃机
CN102072038B (zh) * 2010-12-06 2012-11-21 北京中清能发动机技术有限公司 一种机体以及应用该机体的压缩机、内燃机
CN102220919A (zh) * 2011-05-27 2011-10-19 北京中清能发动机技术有限公司 V型曲柄圆滑块内燃机机体及应用该机体的内燃机
DE102013008790A1 (de) * 2013-05-22 2014-11-27 Audi Ag Kurbelgehäuse für eine Brennkraftmaschine
CN203868143U (zh) * 2013-12-12 2014-10-08 北京中清能发动机技术有限公司 一种轴承座、机体以及应用所述轴承座的往复式柱塞泵
KR20200051812A (ko) 2017-09-18 2020-05-13 엔토믹스 바이오시스템스 리미티드 곤충 유충 사육

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN85100358B (zh) 1985-04-01 1988-01-13 黎正中 曲柄圆滑块往复活塞式内燃机
WO1994013966A1 (en) * 1992-12-09 1994-06-23 Man B&W Diesel A/S A piston engine of the crosshead type
CN1144879A (zh) * 1995-06-13 1997-03-12 黎正中 曲柄双圆滑块往复活塞式内燃机
CN1144880A (zh) 1995-06-13 1997-03-12 黎正中 曲柄多圆滑块往复活塞式内燃机
CN1429981A (zh) * 2002-01-02 2003-07-16 陈玉洲 无磨损台阶缸套
CN101761359A (zh) * 2009-10-22 2010-06-30 北京中清能发动机技术有限公司 曲柄圆滑块机构的v型机体及其缸套、缸套组、机械设备
CN101761409A (zh) * 2009-10-22 2010-06-30 北京中清能发动机技术有限公司 一种用于曲柄圆滑块内燃机的缸套、缸套组及其内燃机

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4270395A (en) * 1977-06-30 1981-06-02 Grundy Reed H Motion translating mechanism
US4173151A (en) * 1977-06-30 1979-11-06 Grundy Reed H Motion translating mechanism
US4850313A (en) * 1988-02-16 1989-07-25 Peter Gibbons Cruciform engine
US5083537A (en) * 1990-12-17 1992-01-28 Ford Motor Company Composite internal combustion engine housing
US5503038A (en) * 1994-04-01 1996-04-02 Aquino; Giovanni Free floating multiple eccentric device
UA50790C2 (uk) * 1999-03-09 2002-11-15 Олексій Феліксович Вуль Поршнева машина з безшатунним механізмом
DE10042217C2 (de) * 2000-08-28 2002-06-20 Knorr Bremse Systeme Kolbenkompressor für Fahrzeuge (Kolbenbefestigungsanordnung)
WO2008018806A1 (en) * 2006-08-09 2008-02-14 Whisper Tech Limited A reciprocating piston machine with oscillating balancing rotors
WO2008085920A2 (en) 2007-01-05 2008-07-17 Efficient-V, Inc. Motion translation mechanism
CN101503966A (zh) * 2008-10-23 2009-08-12 唐人忠 用于活塞式内燃发动机或气体压缩机上的气缸连杆机构

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN85100358B (zh) 1985-04-01 1988-01-13 黎正中 曲柄圆滑块往复活塞式内燃机
WO1994013966A1 (en) * 1992-12-09 1994-06-23 Man B&W Diesel A/S A piston engine of the crosshead type
CN1144879A (zh) * 1995-06-13 1997-03-12 黎正中 曲柄双圆滑块往复活塞式内燃机
CN1144880A (zh) 1995-06-13 1997-03-12 黎正中 曲柄多圆滑块往复活塞式内燃机
CN1067741C (zh) 1995-06-13 2001-06-27 辽宁大安发动机研究所 曲柄双圆滑块往复活塞式内燃机
CN1429981A (zh) * 2002-01-02 2003-07-16 陈玉洲 无磨损台阶缸套
CN101761359A (zh) * 2009-10-22 2010-06-30 北京中清能发动机技术有限公司 曲柄圆滑块机构的v型机体及其缸套、缸套组、机械设备
CN101761409A (zh) * 2009-10-22 2010-06-30 北京中清能发动机技术有限公司 一种用于曲柄圆滑块内燃机的缸套、缸套组及其内燃机

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP2492439A4

Also Published As

Publication number Publication date
CN101761359A (zh) 2010-06-30
BR112012009657B1 (pt) 2021-01-19
ES2557579T3 (es) 2016-01-27
US20120266831A1 (en) 2012-10-25
US8931442B2 (en) 2015-01-13
EP2492439B1 (en) 2015-10-14
BR112012009657A2 (pt) 2017-08-29
JP5718343B2 (ja) 2015-05-13
CN101761359B (zh) 2012-05-09
JP2013508602A (ja) 2013-03-07
EP2492439A1 (en) 2012-08-29
EP2492439A4 (en) 2014-10-15

Similar Documents

Publication Publication Date Title
WO2011047526A1 (zh) 曲柄圆滑块机构的v型机体及其缸套、缸套组、机械设备
KR20090032947A (ko) 실린더 헤드
JP2005054685A (ja) 圧縮比可変エンジン
EP2907986A1 (en) A four-stroke internal combustion engine with variable compression ratio
EP2048336B1 (en) Variable stroke engine
EP2021584B1 (en) Internal combustion engine
EP2604889B1 (en) Crank circular sliding block mechanism, parts thereof, and equipment therefrom
EP0653549B1 (en) Four cycle engine
CA2960339C (en) Internal combustion engines
US9587529B2 (en) Engine
EP2635775B1 (en) Internal combustion engine
CZ285414B6 (cs) Objemový stroj
US10240559B2 (en) Piston arrangement and internal combustion engine
JP2008190365A (ja) ユニフロー式２ストローク内燃機関
JP5010742B2 (ja) ピストン機械
US11149629B2 (en) Hybrid engine
US20170045014A1 (en) Multi-piece cylinder
CN101761409B (zh) 一种用于曲柄圆滑块内燃机的缸套、缸套组及其内燃机
CN201574830U (zh) 二冲程曲柄圆滑块内燃机缸套、机体及其内燃机
KR20180013651A (ko) 엔진 무빙 장치
JP2013087933A (ja) 巻掛け部材の支持部材および内燃機関

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 10824367

Country of ref document: EP

Kind code of ref document: A1

WWE Wipo information: entry into national phase

Ref document number: 2012534514

Country of ref document: JP

NENP Non-entry into the national phase

Ref country code: DE

WWE Wipo information: entry into national phase

Ref document number: 3744/DELNP/2012

Country of ref document: IN

WWE Wipo information: entry into national phase

Ref document number: 2010824367

Country of ref document: EP

WWE Wipo information: entry into national phase

Ref document number: 13502904

Country of ref document: US

REG Reference to national code

Ref country code: BR

Ref legal event code: B01A

Ref document number: 112012009657

Country of ref document: BR

ENP Entry into the national phase

Ref document number: 112012009657

Country of ref document: BR

Kind code of ref document: A2

Effective date: 20120424