GB2455543A - Reciprocating machine, eg engine, compressor or expander, with a rectilinear drive mechanism - Google Patents
Reciprocating machine, eg engine, compressor or expander, with a rectilinear drive mechanism Download PDFInfo
- Publication number
- GB2455543A GB2455543A GB0724308A GB0724308A GB2455543A GB 2455543 A GB2455543 A GB 2455543A GB 0724308 A GB0724308 A GB 0724308A GB 0724308 A GB0724308 A GB 0724308A GB 2455543 A GB2455543 A GB 2455543A
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- Prior art keywords
- disclosed
- reciprocating machine
- previous
- piston
- diaphragm
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- 230000007246 mechanism Effects 0.000 title claims abstract description 27
- 238000002485 combustion reaction Methods 0.000 claims abstract description 19
- 150000001875 compounds Chemical class 0.000 claims description 4
- 230000002093 peripheral effect Effects 0.000 claims description 4
- 239000000969 carrier Substances 0.000 description 6
- 238000000034 method Methods 0.000 description 6
- 238000010009 beating Methods 0.000 description 4
- 230000008901 benefit Effects 0.000 description 4
- 239000012530 fluid Substances 0.000 description 4
- 238000004519 manufacturing process Methods 0.000 description 4
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 238000006073 displacement reaction Methods 0.000 description 2
- 230000037361 pathway Effects 0.000 description 2
- 230000000717 retained effect Effects 0.000 description 2
Classifications
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- 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
- F01B9/026—Rigid connections between piston and rod; Oscillating pistons
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- 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
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- 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
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- 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
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Compressor (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
Abstract
A reciprocating machine, such as an internal combustion engine, a compressor or expander, is operated by a rectilinear drive mechanism. Each piston is connected to a slider block 4 of the rectilinear drive mechanism by means of a piston rod 3, the free end of which is connected to the slider block 4 via a palm bearing. The palm bearing consists of arcuate surfaces on the free end of piston rod 3 and on palm support 5 which is rigidly attached to slider block 4. A second feature of the invention is that a diaphragm 12 is fitted to the piston 1 to provide a substantially flat surface beneath the piston. The piston rod 3 passes through a guide 13 in second diaphragm 14. The diaphragms provide a working volume 11 below the piston 1 making the piston double acting.
Description
A Piston Rod Assembly for a Reciprocating Machine ooerated by a Rectilinear Drive Mechanism
Field of the invention
The present invention relates to the use of a rectilinear drive mechanism in a reciprocating machine such as an internal combustion engine, a compressor or expander having a plurality of cylinders in which pistons are connected to the carriers or slider blocks of the rectilinear drive mechanism by piston rods.
Background
It is known that a rectilinear drive mechanism (see Definitions and Terminology) can be used to provide reciprocating motion in a positive displacement machine such as an internal combustion engine, expander or compressor. The pistons in such mechanisms are connected to slider blocks or carriers by piston rods of various configurations. The present invention deals with specific aspects of the design of the piston rod, slider block and piston assembly.
Definitions and Terminology In the context of this invention, the following tenns are used.
A rectilinear drive mechanism is an assembly comprising a crankshaft fitted with paired discs or stepped discs (usually cylindrically shaped and fixed together) which can rotate about the crankpin of the crankshaft, in an orbital fashion, each disc of the pair being guided and constrained by at least one linear rail and the rail(s) of each disc being orthogonal to each other. The direction of rotation of the paired discs is opposite to that of the crankshaft. The motion of the centre of each disc is linear and reciprocating and is orthogonal to that of the other disc in the paired disc assembly.
A slider block or carrier is a component of a rectilinear drive mechanism having at least one flat external surface engaged with a guide to ensure rectilinear motion and a cylindrical internal surface which acts as a bearing in which one of a pair of discs is rotatably mounted.
An arcuate surface is a two or three dimensionally curved surface which may represent a part of a cylinder, sphere, spheroid, or ellipsoid but which may not be geometrically perfect in that representation.
Fracture splitting is a production technique involving the creation of an accurately matching joint with self locating surfaces between two components by breaking one component into two pieces in a controlled manner. The surfaces so formed can be described as fracture split surfaces.
A palm bearing is a joint between two surfaces which are transmitting predominantly compressive loads whereby the joint has substantially matching arcuate surfaces allowing for minor angular movement between the components.
A piston pin is a substantially cylindrical component which engages with a piston and a piston rod connecting the two components together but allowing relative rotational movement.
A check valve is a device that only allows uni-directional gas flow; any reverse flow closes the check valve until flow is re- established in the first direction. Iofl
Ports are flow passages allowing gas to move in either one or the opposite direction depending on the direction of the pressure drop across the port Pnor Art Rectilinear diive mechanisms exist in the field of engines and an example of such an application can be found in European Patent number 0493 135A1. A further example is disclosed in GB application number 0722881.0. Both of these applications acknowledge the need to accommodate any unintentional misalignment between the axis of movement of the slider block and the axis of movement of the piston. The current invention provides an alternative means of accommodating that misaligmnent. The current invention also builds on the benefits of the reciprocating machines disclosed in the above prior art by allowing the volume displaced by the underside of the piston(s) to be used for compressing or expanding the working fluid, for example, in a compressor, expander or two-stroke engine configuration.
Summary of the invention
The broadest aspect of the invention comprises a reciprocating machine containing at least one cylinder and at least one rectilinear drive mechanism and at least one piston 1 and at least one piston rod 3, 50 characterised in that the free end of said piston rod 3, 50 is connected to slider block 4 via palm beating 33, 37, 56, 57.
This invention is described, with various embodiments, in the following figures and text
Brief Description of Figures
Figure 1 shows a front view of a piston, piston rod and slider block assembly located in a cylinder bore.
Figure 2 shows a front sectional view of a first embodiment palm bearing assembly.
Figure 3 shows a side sectional view of the first embodiment palm bearing assembly.
Figure 4 shows a front sectional view of a second embodiment palm bearing assembly.
Figure 5 shows a side sectional view of the second embodiment palm bearing assembly.
Detailed Description of the Preferred Embodiments
With reference to Figure 1, piston I is located in cylinder bore 2 and is rigidly attached or monolithic with piston rod 3. Slider block 4 is a part of a rectilinear drive mechanism (not shown) and thus reciprocates with substantially simple hannonic motion in direction 16. Palm carrierS is rigidly attached to slider block 4, for example, by two bolts (not shown) on axes 9 and 10. Slider block 4 is preferably made in two parts 19 and 20 with the join between them being substantially along axis 18. This enables slider block 4 to be assembled onto a disc (not shown) which is part of the rectilinear drive mechanism (not shown). Parts 19 and 20 may be made by the crack splitting technique as detailed in GB patent application number 0722881.0 and, if so, holes 7 and 8 are located substantially on axis 18 at positions between bore 6 and the sides 21 and 22 of slider block 4. The presence of holes 7 and 8 assists the crack splitting process and guides the crack along the desired pathway. Parts 19 and 20 are preferably rigidly attached together using the same fixings on axes 9 and 10 as are used for the attachment of palm carrier 5.
Figure 2 shows a detail of the palm beating arrangement at the join between piston rod 3 and palm carrier 5. Figure 2 is a sectional view corresponding to the view shown in Figure 1 but 2of7 is to a different scale. Referring to Figure 2, piston rod 3 has an arcuate surface 33 at its bottom or free end and when under compressive load is in contact with a substantially matching arcuate surface 37 on palm support 5. Pin 35 protrudes from the free end of piston rod 3 and engages with hole 34in palm support 5. Head 36 on pin 35 prevents pin 35 from withdrawing from hole 34. Pin 35 is preferably press fitted into a hole (not shown) in the free end of piston rod 3. The upper surface 39 of head 36 and the inner surface 40 of palm support are preferably aicuate and substantially matching surfaces. In the event of tensile loads being passed through piston rod 3 and slider block 4, upper surface 39 of head 36 and the inner surface 40 of palm support 5 make contact to transmit the loads.
Figure 3 shows a sectional view of the same embodiment on axes 23 and 24 in the direction shown by arrow 32 in Figure 2. Referring to Figure 3 surfaces 33 and 37 are arcuate in this view also. They are, therefore, three dimensionally curved surfaces. They may, for example represent portions of spheres. Upper surface 39 of head 36 and the inner surface 40 of palm support 5 are arcuate in this plane also which means that they are three dimensionally curved and substantially matching surfaces. In most applications of the invention, the loads in the piston rod will be predominantly compressive. The palm bearing surfaces will, therefore, lransmit the loads while allowing movement between principal axis 23 of piston rod 3 and principal axis 24 of slider block 4. The palm bearing arrangement shown in Figures 2 and 3 can be said to allow for 4 dimensional movement in the joint. That is to say that relative movement can occur in directions 15 and 16 (Figure 2) and direction 27 (Figure 3) as well as relative angular movement occurring as illustrated by arrows 25 (Figure 2) and 26 (Figure 3).
Figures 4 and 5 show a second embodiment which has an alternative palm bearing arrangement but is otherwise similar to the first embodiment Figures 4 and 5 show equivalent views to those of Figures 2 and 3 respectively. The second embodiment is a simpler arrangement with the advantage of lower manufacturing cost Referring to Figures 4 and 5, piston rod 50 has a two dimensionally arcuate surface 56 at its bottom or free end and when under compressive load is in contact with a substantially matching two dimensionally arcuate surface 57 on palm support 51. Surfaces 56 and 57 may, for example represent portions of cylinders. Pin 52 protrudes from the free end of piston rod 50 and engages with hole 54 in palm support 51. The upper surface 55 of head 53 and the inner surface 58 of palm support 51 are also preferably two dimensionally arcuate and substantially matching surfaces. In the event of tensile loads being passed through piston rod 50 and slider block 4, upper surface 55 of head 53 and the inner surface 58 of palm support 51 make contact to transmit the loads. As with the first embodiment this embodiment allows for relative four dimensional movement between slider block 4 and piston rod 50.
In Figures 2 to 5 it should be noted that clearances have been shown in an exaggerated form for the purposes of clarity.
Referring again to Figure 1, in some applications of reciprocating machines, for example, 2-stroke internal combustion engines, expanders or compressors, it may be advantageous to have working volumes on both sides of piston 1. The principal working volume will be above (as seen in Figure 1) piston 1 but in the embodiment shown an additional working volume 11 is provided below piston 1, bounded by first diaphragm 12, cylinder bore 2 and second diaphragm 14. Piston rod 3 is engaged with guide 13 which also contains a seal (not shown).
Guide 13 is supported within diaphragm 14. First diaphragm 12 and second diaphragm 14 preferably have substantially fiat matching surfaces which enables them to approach each other closely at the bottom of the piston stroke so that a high compression ratio can be achieved. Valve means are required to allow the working fluid to enter and leave volume 11.
These may, for example, be in the form of passive check valves in diaphragm 14 or ports in cylinder bore 2 covered an uncovered by piston 1. These types of valve means are well known and are not shown in Figure 1. 3of7
With regard to any of the Figures it is preferable that palm bearing 33, 37, 56, 57 consists of arcuate surface 33, 56 on the free end of piston rod 3, 50 and arcuate surface 37, 57 on palm support 5, 51 which is rigidly attached to slider block 4. However, it should be noted that the palm bearing arrangement may be inverted such that the palm bearing consists of a arcuate surfaces on slider block 4 and palm support 5, 51 which is rigidly attached to the free end of piston rod 3, 50. In this case pin 35, 52 would be fixed to slider block 4 and inverted relative to the embodiments shown in the figures.
In an alternative embodiment piston rod 3, 50 may be connected to piston 1 by means of a piston pin having its major axis orthogonal to the major axis 24 of slider block 4 Pin 35, 52 is located with clearance within hole 34, in palm support 5, 51 and is consirained within the palm support by means of head 36,53 which is of larger diameter than the hole 34,54 inthe palm support 5,51.
Slider block 4 is preferably made in two parts 19, 20 by fracture splitting and the slider block 4 has at least one hole 7, 8 located between bearing bore 6 and sides 21,22 of slider block 4 which is substantially orthogonal to the axis 18 of the fracture split. The two parts 19, 20 of slider block 4 are preferably attached together and to palm support 5, 51 using the same fixings.
The underside of piston 1 is fitted with a first diaphragm 12 which is rigid and is sealed around piston rod 3,50. First diaphragm 12 is attached to piston 1 by shrink fit. The shrink fit may be only between the outer diameter of the first diaphragm and the inner diameter of the piston. First diaphragm 12 may be attached to piston rod 3, 50 by shrink fit. The shrink fit may be between the inner diameter of the first diaphragm and the outer peripheiy of the piston rod.
Piston rod 3,50 passes through guide 13 which is fitted with a seal and which is mounted in second diaphragm 14 which encloses working volume 11 between the second diaphragm 14, cylinder bore 2 and piston I or first diaphragm 12.
At least one gas exchange valve may operate within second diaphragm 14 or cylinder bore 2.
The first diaphragm may be attached to the piston by a circlip and peripheral spring. The circip and spring may be between the first diaphragm and the piston. The circlip and spring may be between the first diaphragm and the piston rod.
Any of the embodiments of the invention may be part of a single or double acting compressor, a single or double acting expander,. an internal combustion engine, a pressure charged internal combustion engine, a compound expansion internal combustion engine or a Stirling cycle engine.
With reference to Figure 1 a gapless top piston ring may be used. A gapless bottom ring may be fitted and this may be retained by the first diaphragm. Gas exchange valves may be attached to the second diaphragm.
The previously described piston and piston rod may be connected to palm bearings that are attached with fixings to slider blocks that are monolithic and not split. 4of7 aaims
A Piston Rod Assembly for a Reciprocating Machine ooerated by a Rectilinear Drive Mechanism
Field of the invention
The present invention relates to the use of a rectilinear drive mechanism in a reciprocating machine such as an internal combustion engine, a compressor or expander having a plurality of cylinders in which pistons are connected to the carriers or slider blocks of the rectilinear drive mechanism by piston rods.
Background
It is known that a rectilinear drive mechanism (see Definitions and Terminology) can be used to provide reciprocating motion in a positive displacement machine such as an internal combustion engine, expander or compressor. The pistons in such mechanisms are connected to slider blocks or carriers by piston rods of various configurations. The present invention deals with specific aspects of the design of the piston rod, slider block and piston assembly.
Definitions and Terminology In the context of this invention, the following tenns are used.
A rectilinear drive mechanism is an assembly comprising a crankshaft fitted with paired discs or stepped discs (usually cylindrically shaped and fixed together) which can rotate about the crankpin of the crankshaft, in an orbital fashion, each disc of the pair being guided and constrained by at least one linear rail and the rail(s) of each disc being orthogonal to each other. The direction of rotation of the paired discs is opposite to that of the crankshaft. The motion of the centre of each disc is linear and reciprocating and is orthogonal to that of the other disc in the paired disc assembly.
A slider block or carrier is a component of a rectilinear drive mechanism having at least one flat external surface engaged with a guide to ensure rectilinear motion and a cylindrical internal surface which acts as a bearing in which one of a pair of discs is rotatably mounted.
An arcuate surface is a two or three dimensionally curved surface which may represent a part of a cylinder, sphere, spheroid, or ellipsoid but which may not be geometrically perfect in that representation.
Fracture splitting is a production technique involving the creation of an accurately matching joint with self locating surfaces between two components by breaking one component into two pieces in a controlled manner. The surfaces so formed can be described as fracture split surfaces.
A palm bearing is a joint between two surfaces which are transmitting predominantly compressive loads whereby the joint has substantially matching arcuate surfaces allowing for minor angular movement between the components.
A piston pin is a substantially cylindrical component which engages with a piston and a piston rod connecting the two components together but allowing relative rotational movement.
A check valve is a device that only allows uni-directional gas flow; any reverse flow closes the check valve until flow is re- established in the first direction. Iofl
Ports are flow passages allowing gas to move in either one or the opposite direction depending on the direction of the pressure drop across the port Pnor Art Rectilinear diive mechanisms exist in the field of engines and an example of such an application can be found in European Patent number 0493 135A1. A further example is disclosed in GB application number 0722881.0. Both of these applications acknowledge the need to accommodate any unintentional misalignment between the axis of movement of the slider block and the axis of movement of the piston. The current invention provides an alternative means of accommodating that misaligmnent. The current invention also builds on the benefits of the reciprocating machines disclosed in the above prior art by allowing the volume displaced by the underside of the piston(s) to be used for compressing or expanding the working fluid, for example, in a compressor, expander or two-stroke engine configuration.
Summary of the invention
The broadest aspect of the invention comprises a reciprocating machine containing at least one cylinder and at least one rectilinear drive mechanism and at least one piston 1 and at least one piston rod 3, 50 characterised in that the free end of said piston rod 3, 50 is connected to slider block 4 via palm beating 33, 37, 56, 57.
This invention is described, with various embodiments, in the following figures and text
Brief Description of Figures
Figure 1 shows a front view of a piston, piston rod and slider block assembly located in a cylinder bore.
Figure 2 shows a front sectional view of a first embodiment palm bearing assembly.
Figure 3 shows a side sectional view of the first embodiment palm bearing assembly.
Figure 4 shows a front sectional view of a second embodiment palm bearing assembly.
Figure 5 shows a side sectional view of the second embodiment palm bearing assembly.
Detailed Description of the Preferred Embodiments
With reference to Figure 1, piston I is located in cylinder bore 2 and is rigidly attached or monolithic with piston rod 3. Slider block 4 is a part of a rectilinear drive mechanism (not shown) and thus reciprocates with substantially simple hannonic motion in direction 16. Palm carrierS is rigidly attached to slider block 4, for example, by two bolts (not shown) on axes 9 and 10. Slider block 4 is preferably made in two parts 19 and 20 with the join between them being substantially along axis 18. This enables slider block 4 to be assembled onto a disc (not shown) which is part of the rectilinear drive mechanism (not shown). Parts 19 and 20 may be made by the crack splitting technique as detailed in GB patent application number 0722881.0 and, if so, holes 7 and 8 are located substantially on axis 18 at positions between bore 6 and the sides 21 and 22 of slider block 4. The presence of holes 7 and 8 assists the crack splitting process and guides the crack along the desired pathway. Parts 19 and 20 are preferably rigidly attached together using the same fixings on axes 9 and 10 as are used for the attachment of palm carrier 5.
Figure 2 shows a detail of the palm beating arrangement at the join between piston rod 3 and palm carrier 5. Figure 2 is a sectional view corresponding to the view shown in Figure 1 but 2of7 is to a different scale. Referring to Figure 2, piston rod 3 has an arcuate surface 33 at its bottom or free end and when under compressive load is in contact with a substantially matching arcuate surface 37 on palm support 5. Pin 35 protrudes from the free end of piston rod 3 and engages with hole 34in palm support 5. Head 36 on pin 35 prevents pin 35 from withdrawing from hole 34. Pin 35 is preferably press fitted into a hole (not shown) in the free end of piston rod 3. The upper surface 39 of head 36 and the inner surface 40 of palm support are preferably aicuate and substantially matching surfaces. In the event of tensile loads being passed through piston rod 3 and slider block 4, upper surface 39 of head 36 and the inner surface 40 of palm support 5 make contact to transmit the loads.
Figure 3 shows a sectional view of the same embodiment on axes 23 and 24 in the direction shown by arrow 32 in Figure 2. Referring to Figure 3 surfaces 33 and 37 are arcuate in this view also. They are, therefore, three dimensionally curved surfaces. They may, for example represent portions of spheres. Upper surface 39 of head 36 and the inner surface 40 of palm support 5 are arcuate in this plane also which means that they are three dimensionally curved and substantially matching surfaces. In most applications of the invention, the loads in the piston rod will be predominantly compressive. The palm bearing surfaces will, therefore, lransmit the loads while allowing movement between principal axis 23 of piston rod 3 and principal axis 24 of slider block 4. The palm bearing arrangement shown in Figures 2 and 3 can be said to allow for 4 dimensional movement in the joint. That is to say that relative movement can occur in directions 15 and 16 (Figure 2) and direction 27 (Figure 3) as well as relative angular movement occurring as illustrated by arrows 25 (Figure 2) and 26 (Figure 3).
Figures 4 and 5 show a second embodiment which has an alternative palm bearing arrangement but is otherwise similar to the first embodiment Figures 4 and 5 show equivalent views to those of Figures 2 and 3 respectively. The second embodiment is a simpler arrangement with the advantage of lower manufacturing cost Referring to Figures 4 and 5, piston rod 50 has a two dimensionally arcuate surface 56 at its bottom or free end and when under compressive load is in contact with a substantially matching two dimensionally arcuate surface 57 on palm support 51. Surfaces 56 and 57 may, for example represent portions of cylinders. Pin 52 protrudes from the free end of piston rod 50 and engages with hole 54 in palm support 51. The upper surface 55 of head 53 and the inner surface 58 of palm support 51 are also preferably two dimensionally arcuate and substantially matching surfaces. In the event of tensile loads being passed through piston rod 50 and slider block 4, upper surface 55 of head 53 and the inner surface 58 of palm support 51 make contact to transmit the loads. As with the first embodiment this embodiment allows for relative four dimensional movement between slider block 4 and piston rod 50.
In Figures 2 to 5 it should be noted that clearances have been shown in an exaggerated form for the purposes of clarity.
Referring again to Figure 1, in some applications of reciprocating machines, for example, 2-stroke internal combustion engines, expanders or compressors, it may be advantageous to have working volumes on both sides of piston 1. The principal working volume will be above (as seen in Figure 1) piston 1 but in the embodiment shown an additional working volume 11 is provided below piston 1, bounded by first diaphragm 12, cylinder bore 2 and second diaphragm 14. Piston rod 3 is engaged with guide 13 which also contains a seal (not shown).
Guide 13 is supported within diaphragm 14. First diaphragm 12 and second diaphragm 14 preferably have substantially fiat matching surfaces which enables them to approach each other closely at the bottom of the piston stroke so that a high compression ratio can be achieved. Valve means are required to allow the working fluid to enter and leave volume 11.
These may, for example, be in the form of passive check valves in diaphragm 14 or ports in cylinder bore 2 covered an uncovered by piston 1. These types of valve means are well known and are not shown in Figure 1. 3of7
With regard to any of the Figures it is preferable that palm bearing 33, 37, 56, 57 consists of arcuate surface 33, 56 on the free end of piston rod 3, 50 and arcuate surface 37, 57 on palm support 5, 51 which is rigidly attached to slider block 4. However, it should be noted that the palm bearing arrangement may be inverted such that the palm bearing consists of a arcuate surfaces on slider block 4 and palm support 5, 51 which is rigidly attached to the free end of piston rod 3, 50. In this case pin 35, 52 would be fixed to slider block 4 and inverted relative to the embodiments shown in the figures.
In an alternative embodiment piston rod 3, 50 may be connected to piston 1 by means of a piston pin having its major axis orthogonal to the major axis 24 of slider block 4 Pin 35, 52 is located with clearance within hole 34, in palm support 5, 51 and is consirained within the palm support by means of head 36,53 which is of larger diameter than the hole 34,54 inthe palm support 5,51.
Slider block 4 is preferably made in two parts 19, 20 by fracture splitting and the slider block 4 has at least one hole 7, 8 located between bearing bore 6 and sides 21,22 of slider block 4 which is substantially orthogonal to the axis 18 of the fracture split. The two parts 19, 20 of slider block 4 are preferably attached together and to palm support 5, 51 using the same fixings.
The underside of piston 1 is fitted with a first diaphragm 12 which is rigid and is sealed around piston rod 3,50. First diaphragm 12 is attached to piston 1 by shrink fit. The shrink fit may be only between the outer diameter of the first diaphragm and the inner diameter of the piston. First diaphragm 12 may be attached to piston rod 3, 50 by shrink fit. The shrink fit may be between the inner diameter of the first diaphragm and the outer peripheiy of the piston rod.
Piston rod 3,50 passes through guide 13 which is fitted with a seal and which is mounted in second diaphragm 14 which encloses working volume 11 between the second diaphragm 14, cylinder bore 2 and piston I or first diaphragm 12.
At least one gas exchange valve may operate within second diaphragm 14 or cylinder bore 2.
The first diaphragm may be attached to the piston by a circlip and peripheral spring. The circip and spring may be between the first diaphragm and the piston. The circlip and spring may be between the first diaphragm and the piston rod.
Any of the embodiments of the invention may be part of a single or double acting compressor, a single or double acting expander,. an internal combustion engine, a pressure charged internal combustion engine, a compound expansion internal combustion engine or a Stirling cycle engine.
With reference to Figure 1 a gapless top piston ring may be used. A gapless bottom ring may be fitted and this may be retained by the first diaphragm. Gas exchange valves may be attached to the second diaphragm.
The previously described piston and piston rod may be connected to palm bearings that are attached with fixings to slider blocks that are monolithic and not split. 4of7 aaims
Claims (1)
1 A reciprocating machine containing at least one cylinder and at least one rectilinear drive mechanism and at least one piston 1 and at least one piston rod 3, 50 characterised in that the free end of said piston rod 3, 50 is connected to slider block 4 via palm bearing 33, 37, 56, 57.
2 A reciprocating machine as disclosed in Claim 1 in which the said palm bearing consists of arcuate surface 33, 56 on the free end of piston rod 3, 50 and arcuate surface 37,57 on palm support 5, 51 which is rigidly attached to slider block 4.
3 A reciprocating machine as disclosed in Claim 1 in which the said palm bearing consists of arcuate surfaces on slider block 4 and palm support 5, 51 which is rigidly attached to the free end of piston rod 3, 50.
4 A reciprocating machine as disclosed in any previous claim in which palm bearing 33, 37, 56, 57 allows four degrees of freedom of movement 15, 16, 25, 26, 27.
A reciprocating machine as disclosed in any previous claim in which piston rod 3, 50 and piston I are monolithic or rigidly attached together.
6 A reciprocating machine as disclosed in any previous claim in which piston rod 3, 50 is connected to piston 1 by means of a piston pin 7 A reciprocating machine as disclosed in any previous claim in which the palm bearing has substantially matching arcuate surfaces 33, 37, 56, 57.
8 A reciprocating machine as disclosed in any previous claim in which the free end of piston rod 3 has a protruding pin which is located with clearance within hole 34,54 in palm support 5, 51 and which is constrained within said palm support by means of head 36, 53 which is of larger diameter than.said hole 34,54 in said palm support 5, 51.
9 A reciprocating machine as disclosed in any previous claim in which palm support 5, 51 is rigidly attached to slider block 4.
A reciprocating machine as disclosed in any previous claim in which slider block 4 is made in two parts 19, 20 by fracture splitting and said slider block 4 has at least one hole 7, 8 located between bearing bore 6 and sides 21, 22 of slider block 4 which is substantially orthogonal to the axis 18 of the fracture split.
11 A reciprocating machine as disclosed in Claim 10 in which the two parts 19,20 of slider block 4 are attached together and to palm support 5, 51 using the same fixings.
12 A reciprocating machine as disclosed in any previous claim in which the underside of the piston is fitted with a first diaphragm 12 which is rigid and is sealed around piston rod 3,50.
13 A reciprocating machine as disclosed in Claim 12 in which first diaphragm 12 is attached to piston 1 by shrink fit.
14 A reciprocating machine as disclosed in Claims 12 or 13 in which first diaphragm 12 is attached to piston rod 3,50 by shrink fit. 50f7
A reciprocating machine as disclosed in any previous claim in which piston rod 3, 50 passes through guide 13 which is fitted with a seal and which is mounted in second diaphragm 14 which encloses working volume 11 between said second diaphragm 14, cyLinder bore 2 and piston 1 or first diaphragm 12.
16 A reciprocating machine as disclosed in any previous claim in which at least one gas exchange valve operates within second diaphragm 14 or cylinder bore 2.
17 A reciprocating machine as disclosed in Claim 13 in which the shrink fit is only between the outer diameter of the first diaphragm and the inner diameter of the piston.
18 A reciprocating machine as disclosed in Claim 14 in which the shrink fit is between the inner diameter of the first diaphragm and the outer periphery of the piston rod.
19 A reciprocating machine as disclosed in any previous claim in which the first diaphragm is attached to the piston by a circip and peripheral spring.
A reciprocating machine as disclosed in Claim 19 in which the circlip and spring are between the first diaphragm and the piston.
21 A reciprocating machine as disclosed in Claim 19 in which the circip and spring are between the first diaphragm and the piston rod.
22 A reciprocating machine as disclosed in any previous claim when used as part of a double acting compressor.
23 A reciprocating machine as disclosed in any previous claim when used as a double acting expander.
24 A reciprocating machine as disclosed in any previous claim when used as part of an internal combustion engine.
A reciprocating machine as disclosed in any previous claim when used as part of a pressure charged internal combustion engine.
26 A reciprocating machine as disclosed in any previous claim when used as part of a compound expansion internal combustion engine.
27 A reciprocating machine as disclosed in any previous claim when used as part of a Stirling cycle engine.
28 A reciprocating machine as disclosed in any previous claim in which a gapless top piston ring is used.
29 A reciprocating machine as disclosed in any previous claim in which a gapless bottom ring is fitted.
A reciprocating machine as disclosed in Claim 29 in which the first diaphragm retains the gapless bottom ring.
31 A reciprocating machine as disclosed in any previous claim in which gas exchange valves are attached to the second diaphragm. 6of7
1 A reciprocating machine containing at least one cylinder and at least one rectilinear drive mechanism and at least one piston 1 and at least one piston rod 3, 50 characterised in that the free end of said piston rod 3, 50 is connected to slider block 4 via palm bearing 33, 37, 56, 57.
2 A reciprocating machine as disclosed in Claim 1 in which the said palm bearing consists of arcuate surface 33, 56 on the free end of piston rod 3, 50 and arcuate surface 37,57 on palm support 5, 51 which is rigidly attached to slider block 4.
3 A reciprocating machine as disclosed in Claim 1 in which the said palm bearing consists of arcuate surfaces on slider block 4 and palm support 5, 51 which is rigidly attached to the free end of piston rod 3, 50.
4 A reciprocating machine as disclosed in any previous claim in which palm bearing 33, 37, 56, 57 allows four degrees of freedom of movement 15, 16, 25, 26, 27.
A reciprocating machine as disclosed in any previous claim in which piston rod 3, 50 and piston I are monolithic or rigidly attached together.
6 A reciprocating machine as disclosed in any previous claim in which piston rod 3, 50 is connected to piston 1 by means of a piston pin 7 A reciprocating machine as disclosed in any previous claim in which the palm bearing has substantially matching arcuate surfaces 33, 37, 56, 57.
8 A reciprocating machine as disclosed in any previous claim in which the free end of piston rod 3 has a protruding pin which is located with clearance within hole 34,54 in palm support 5, 51 and which is constrained within said palm support by means of head 36, 53 which is of larger diameter than.said hole 34,54 in said palm support 5, 51.
9 A reciprocating machine as disclosed in any previous claim in which palm support 5, 51 is rigidly attached to slider block 4.
A reciprocating machine as disclosed in any previous claim in which slider block 4 is made in two parts 19, 20 by fracture splitting and said slider block 4 has at least one hole 7, 8 located between bearing bore 6 and sides 21, 22 of slider block 4 which is substantially orthogonal to the axis 18 of the fracture split.
11 A reciprocating machine as disclosed in Claim 10 in which the two parts 19,20 of slider block 4 are attached together and to palm support 5, 51 using the same fixings.
12 A reciprocating machine as disclosed in any previous claim in which the underside of the piston is fitted with a first diaphragm 12 which is rigid and is sealed around piston rod 3,50.
13 A reciprocating machine as disclosed in Claim 12 in which first diaphragm 12 is attached to piston 1 by shrink fit.
14 A reciprocating machine as disclosed in Claims 12 or 13 in which first diaphragm 12 is attached to piston rod 3,50 by shrink fit. 50f7
A reciprocating machine as disclosed in any previous claim in which piston rod 3, 50 passes through guide 13 which is fitted with a seal and which is mounted in second diaphragm 14 which encloses working volume 11 between said second diaphragm 14, cyLinder bore 2 and piston 1 or first diaphragm 12.
16 A reciprocating machine as disclosed in any previous claim in which at least one gas exchange valve operates within second diaphragm 14 or cylinder bore 2.
17 A reciprocating machine as disclosed in Claim 13 in which the shrink fit is only between the outer diameter of the first diaphragm and the inner diameter of the piston.
18 A reciprocating machine as disclosed in Claim 14 in which the shrink fit is between the inner diameter of the first diaphragm and the outer periphery of the piston rod.
19 A reciprocating machine as disclosed in any previous claim in which the first diaphragm is attached to the piston by a circip and peripheral spring.
A reciprocating machine as disclosed in Claim 19 in which the circlip and spring are between the first diaphragm and the piston.
21 A reciprocating machine as disclosed in Claim 19 in which the circip and spring are between the first diaphragm and the piston rod.
22 A reciprocating machine as disclosed in any previous claim when used as part of a double acting compressor.
23 A reciprocating machine as disclosed in any previous claim when used as a double acting expander.
24 A reciprocating machine as disclosed in any previous claim when used as part of an internal combustion engine.
A reciprocating machine as disclosed in any previous claim when used as part of a pressure charged internal combustion engine.
26 A reciprocating machine as disclosed in any previous claim when used as part of a compound expansion internal combustion engine.
27 A reciprocating machine as disclosed in any previous claim when used as part of a Stirling cycle engine.
28 A reciprocating machine as disclosed in any previous claim in which a gapless top piston ring is used.
29 A reciprocating machine as disclosed in any previous claim in which a gapless bottom ring is fitted.
A reciprocating machine as disclosed in Claim 29 in which the first diaphragm retains the gapless bottom ring.
31 A reciprocating machine as disclosed in any previous claim in which gas exchange valves are attached to the second diaphragm. 6of7
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| GB0724308A GB2455543A (en) | 2007-12-11 | 2007-12-11 | Reciprocating machine, eg engine, compressor or expander, with a rectilinear drive mechanism |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| GB0724308A GB2455543A (en) | 2007-12-11 | 2007-12-11 | Reciprocating machine, eg engine, compressor or expander, with a rectilinear drive mechanism |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| GB0724308D0 GB0724308D0 (en) | 2008-01-23 |
| GB2455543A true GB2455543A (en) | 2009-06-17 |
Family
ID=39016517
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| GB0724308A Withdrawn GB2455543A (en) | 2007-12-11 | 2007-12-11 | Reciprocating machine, eg engine, compressor or expander, with a rectilinear drive mechanism |
Country Status (1)
| Country | Link |
|---|---|
| GB (1) | GB2455543A (en) |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| BE861533A (en) * | 1977-12-06 | 1978-03-31 | Bullaert Daniel E | NEW DRIVE MECHANISMS FOR OIL-FREE COMPRESSORS AND HEAT PUMPS |
| US4884536A (en) * | 1987-05-29 | 1989-12-05 | Collins Motor Corporation Limited | Interconnecting rotary and reciprocatory motion |
| US6012423A (en) * | 1995-03-14 | 2000-01-11 | Bayerische Motoren Werke Aktiengesellschaft | Hypocycloidal crank mechanism for piston engines, engines especially for opposed-cylinder internal combustion engines |
| EP1170462A1 (en) * | 1999-03-09 | 2002-01-09 | Aleksey Feliksovich Vool | Piston machine comprising a mechanism with no connecting-rod |
-
2007
- 2007-12-11 GB GB0724308A patent/GB2455543A/en not_active Withdrawn
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| BE861533A (en) * | 1977-12-06 | 1978-03-31 | Bullaert Daniel E | NEW DRIVE MECHANISMS FOR OIL-FREE COMPRESSORS AND HEAT PUMPS |
| US4884536A (en) * | 1987-05-29 | 1989-12-05 | Collins Motor Corporation Limited | Interconnecting rotary and reciprocatory motion |
| US6012423A (en) * | 1995-03-14 | 2000-01-11 | Bayerische Motoren Werke Aktiengesellschaft | Hypocycloidal crank mechanism for piston engines, engines especially for opposed-cylinder internal combustion engines |
| EP1170462A1 (en) * | 1999-03-09 | 2002-01-09 | Aleksey Feliksovich Vool | Piston machine comprising a mechanism with no connecting-rod |
Also Published As
| Publication number | Publication date |
|---|---|
| GB0724308D0 (en) | 2008-01-23 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| WAP | Application withdrawn, taken to be withdrawn or refused ** after publication under section 16(1) |