GB2550135A - Axially Loaded spherical Joint assembly - Google Patents

Axially Loaded spherical Joint assembly Download PDF

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Publication number
GB2550135A
GB2550135A GB1608080.6A GB201608080A GB2550135A GB 2550135 A GB2550135 A GB 2550135A GB 201608080 A GB201608080 A GB 201608080A GB 2550135 A GB2550135 A GB 2550135A
Authority
GB
United Kingdom
Prior art keywords
cup
ball
rod
lubrication
formation
Prior art date
Legal status (The legal status 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 status listed.)
Granted
Application number
GB1608080.6A
Other versions
GB2550135B (en
GB201608080D0 (en
Inventor
Beck Robert
Cooper Ian
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Ultra Electronics Ltd
Original Assignee
Ultra Electronics Ltd
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 Ultra Electronics Ltd filed Critical Ultra Electronics Ltd
Priority to GB1608080.6A priority Critical patent/GB2550135B/en
Publication of GB201608080D0 publication Critical patent/GB201608080D0/en
Publication of GB2550135A publication Critical patent/GB2550135A/en
Application granted granted Critical
Publication of GB2550135B publication Critical patent/GB2550135B/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • 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
    • 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
    • F04B39/0005—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 adaptations of pistons
    • 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
    • F04B39/0005—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 adaptations of pistons
    • F04B39/0022—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 adaptations of pistons piston rods
    • 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
    • F04B39/02—Lubrication
    • F04B39/0284—Constructional details, e.g. reservoirs in the casing
    • 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
    • F04B39/02—Lubrication
    • F04B39/0284—Constructional details, e.g. reservoirs in the casing
    • F04B39/0292—Lubrication of pistons or cylinders
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C11/00—Pivots; Pivotal connections
    • F16C11/04—Pivotal connections
    • F16C11/06—Ball-joints; Other joints having more than one degree of angular freedom, i.e. universal joints
    • F16C11/0604—Construction of the male part
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C11/00—Pivots; Pivotal connections
    • F16C11/04—Pivotal connections
    • F16C11/06—Ball-joints; Other joints having more than one degree of angular freedom, i.e. universal joints
    • F16C11/0619—Ball-joints; Other joints having more than one degree of angular freedom, i.e. universal joints the female part comprising a blind socket receiving the male part
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C11/00—Pivots; Pivotal connections
    • F16C11/04—Pivotal connections
    • F16C11/06—Ball-joints; Other joints having more than one degree of angular freedom, i.e. universal joints
    • F16C11/068—Special features relating to lubrication
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2360/00—Engines or pumps
    • F16C2360/44—Centrifugal pumps

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Compressor (AREA)
  • Pivots And Pivotal Connections (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)

Abstract

A ball rod 100, eg for use in a high-pressure gas compressor, comprises a spherical ball portion 104 mounted on one or each end of a rod 102 and received in a cup or socket 114, wherein a circular lubrication formation 110 is provided on a distal portion of the ball portion 104, and wherein the centres of the lubrication formation 110 and the ball portion 104 lie on the longitudinal axis of the rod 102, such that a lubricant well is formed between the lubrication formation 110 and an inner surface of the cup/socket 114. The circular lubrication formation 110 may be in the form of a flat surface, a concave well or a cylindrical well. The circular lubrication formation 110 may have a radiused edge 112. The cup 114 may have a complementary lubrication formation 118, eg a concave or cylindrical well, which could be used with a regular ball rod. The socket and the ball portion may be made from nitrided steel.

Description

AXIALLY LOADED SPHERICAL JOINT ASSEMBLY
Technical Field
The present invention relates to an axially loaded spherical joint assembly for use in a high-pressure gas compressor.
Background to the Invention
Gas compressors are widely used in industry to increase the pressure of gases using simple thermodynamic principles. High-pressure gas compressors are capable of raising gas pressures up to anywhere from a few hundred to several thousand psi.
One such compressor, described in UK patent no. GB2144181B, uses a wobble plate in combination with an axially loaded spherical joint assembly comprising a ball rod (i.e. a rod terminating in a ball portion) which is received in a complementary spherical cup or socket (this assembly is sometimes colloquially referred to as a "ball-end joint assembly") to convert rotational motion from a shaft into linear motion of a piston.
Friction in the axially loaded spherical joint assembly between the ball portion and the cup can cause wear to the cup and ultimately cause irreparable damage to the joint. Compressors of the kind disclosed in GB2144181B are typically provided as sealed units, meaning that failure of any one component within the compressor in service requires complete replacement of the entire unit or module. Damage to the cup is therefore highly undesirable, as it can considerably shorten the life of the compressor, and is potentially dangerous in a high-pressure gas compressor due to the extreme forces and stresses involved.
Accordingly, there is a need for an axially loaded spherical joint assembly for use in high-pressure gas compressors which is less prone to damage arising from friction between its ball and socket portions.
Summary of Invention
According to a first aspect of the present invention there is provided a ball rod for use in a high-pressure gas compressor, the ball rod comprising a rod portion and a substantially spherical ball portion mounted on one end of the rod portion, the ball portion configured to be received in a cup, wherein the ball portion comprises a generally circular lubrication formation provided on a distal portion of the ball portion, and wherein the centres of the lubrication formation and the ball portion lie on a principal longitudinal axis of the rod portion, such that when the ball portion is received within the cup, a lubricant well is formed between the lubrication formation and an inner surface of the cup.
The ball rod of the present invention offers a solution to the problem of providing increased protection for an axially loaded spherical joint assembly during use in a high-pressure gas compressor from frictional wear and damage.
The lubrication formation of the ball portion may comprise a flat surface.
The lubrication formation of the ball portion may alternatively comprise a concave well.
The lubrication formation of the ball portion may comprise a radiused edge.
The ball portion may be constructed from a metallic material.
The ball portion may be constructed from nitrided steel.
According to a second aspect of the present invention there is provided a cup for receiving a ball rod according to the first aspect, the cup comprising an inner surface, wherein the inner surface comprises a lubrication formation, such that when the ball rod is received within the cup, a lubricant well is formed between the lubrication formation of the cup and a surface of the ball rod.
The lubrication formation of the cup may comprise a cylindrical well.
The cup may be constructed from a metallic material.
The cup may be constructed from nitrided steel.
According to a third aspect of the invention there is provided an axially loaded spherical joint assembly comprising a ball rod according to the first aspect and a cup according to the second aspect.
According to a fourth aspect of the invention there is provided a high-pressure gas compressor comprising an axially loaded spherical joint assembly according to the third aspect.
Brief Description of the Drawings
Embodiments of the invention will now be described, strictly by way of example only, with reference to the accompanying drawings, of which:
Figure 1 is a schematic perspective view of a ball rod having a lubrication formation;
Figure 2 is a schematic cutaway cross-sectional view of the ball rod illustrated in Figure 1, installed in a complementarycup;
Figure 3 is a schematic perspective view of a ball rod according to another embodiment, having two ball portions and an interconnecting rod portion; and
Figure 4 is a schematic cutaway cross-sectional view of the ball rod illustrated in Figure 4, with both ball portions installed in complementary cups.
Description of the Embodiments
Referring first to Figure 1, a ball rod is shown generally at 100. The ball rod 100 is particularly suitable for use in a high-pressure gas compressor, though it will be appreciated that the ball rod 100 is equally suitable for other applications. The ball rod 100 is configured to be received in a cup or socket, which may be a cup or socket comprising a complementary lubrication formation, as will be described in greater detail below.
The ball rod 100 comprises a rod portion 102 and a substantially spherical ball portion 104, the ball portion 104 being connected to a first end of the rod portion 102. The ball portion 104 is constructed from a hard material, such as a metal. For example, the ball portion 104 may be constructed from nitrided steel.
The ball portion 104 comprises a proximal end 106, to which the rod portion 102 is connected, and a distal end 108. The distal end of the ball portion 108 includes a lubrication formation 110, which is generally circular in shape. In the illustrated embodiment, the lubrication formation 110 has a radiused edge 112. The radiused edge provides a smoothly graduated surface which engages with the cup, thereby reducing the risk of points of high friction between the ball portion and the cup. However, in alternative embodiments the radiused edge need not be provided. The centres of the ball portion 104 and the lubrication formation 110 both lie on a principal longitudinal axis 103 of the rod portion 102.
As can be seen from Figure 2, the ball portion 104 of the ball rod 100 is received within a cup 114. The cup 114 may be constructed from a metallic material, such as nitrided steel. Upon being received within the cup 114, a lubricant well 116 is formed between the lubrication formation 110 and an inner surface of the cup 114. During use, the lubricant well 116 contains a lubricant, such as grease. As the ball portion 104 moves in the cup 114, the lubricant is disposed over the surfaces of the ball portion and cup, reducing friction on the ball portion 104 and the inner surface of the cup 114. As the ball portion 104 rotates relative to the cup 114 during normal use, the lubricant well 116 ensures that the lubricant is dispensed evenly between the ball portion 104 and the inner surface of the cup 114, reducing the friction over the whole of the ball and cup surfaces, and hence reducing the risk of damage to the inner surface of the cup 114. To achieve this effect of increased efficiency of lubrication, the lubrication formation 110 of the ball portion 104 may comprise a generally flat surface on the ball portion 104, the generally flat surface having a generally circular perimeter. Alternatively, the lubrication formation may comprise a concave well on the ball portion 104, again with a generally circular perimeter. Use of a concave well lubrication formation may allow more lubricant to be contained in the lubricant well. Alternatively, the lubrication formation 110 may comprise a substantially cylindrical well. Alternatively still, the lubrication formation 110 may have a different shape.
Although the lubrication formation 110 is shown as being of a particular size relative to the ball portion 104, it will be appreciated by those skilled in the art that the lubrication formation 110 could be of any size relative to the ball portion 104, provided that it is of an adequate size for the lubrication effect to take place.
In the illustrated embodiment, the lubrication formation 110 is axisymmetrical about the major longitudinal axis of the ball-end joint 100, and has a generally circular perimeter. This axisymmetrical arrangement offers the advantage of ensuring that the lubricant is distributed evenly across the surface of the ball portion 104 and the inner surface of the cup. Additionally, the axisymmetrical arrangement of the lubrication formation 110 prevents the occurrence of areas of high point pressure between the ball portion 104 and cup 114, as there are no sharp points on the ball portion 104 which could act as a focal point for pressure. Thus the risk of damage to the cup 114 is reduced. The risk of damage may be further mitigated through the use of a radiused edge 112 running the length of the perimeter of the lubrication feature 110, which provides a smoothly graduated surface around the perimeter of the lubrication feature 110, although it will be appreciated by those skilled in the art that the ball-end joint 100 may equally be constructed without a radiused edge 112 along the perimeter of the lubrication formation 110.
The ball rod 100 may be received within a cup having a complementary lubrication formation 118 of the kind shown in Figure 2. The complementary lubrication formation 118 may comprise a concave well, or it may alternatively comprise a cylindrical well. Alternatively still, the complementary lubrication formation 118 may have a different shape. Although the cup including a complementary lubrication formation 118 has so far been described as being for use in conjunction with the new ball rod comprising a lubrication formation 110, it will be appreciated by those skilled in the art that the cup comprising a complementary lubrication formation may equally be used in conjunction with a regular ball rod.
Referring now to Figures 3 and 4, an alternative embodiment of a ball rod according to the present invention is shown generally at 200. In this alternative embodiment, the ball rod 200 comprises a rod portion 202, the rod portion 202 comprising a first end and a second end. Connected to the first end is a substantially spherical first ball portion 204, and connected to the second end is a substantially spherical second ball portion 206. As will be appreciated from Figures 3 and 4, the first ball portion 204 is substantially identical to the ball portion 104 described above with reference to Figure 1. Similarly, the second ball portion 206 is also substantially identical to the ball portion 104 described above with reference to Figure 1.
Each of the first and second ball portions 204, 206 comprise a respective proximal end 208, 210 to which the rod is connected, and a respective distal end 212, 214. Each respective distal end comprises a lubrication formation 216, 218, each of which is substantially identical to that described above with reference to Figure 1. The centre of each lubrication formation 216, 218 and each of the first and second ball portions 204, 206 lies on a principal longitudinal axis 203 of the rod portion 202.
Referring now to Figure 5, the ball rod 200 described above is shown in situ, having been installed in, for example, a high-pressure gas compressor. Each of the first and second ball portions 204, 206 is installed in a respective cup 220, 222, and each cup 220, 222 may include a complementary lubrication formation 224, 226 of the kind described above with reference to Figure 2. A lubricant well is formed between each lubrication formation 224, 226 and the inner surface of each cup. These lubricant wells are substantially identical to, and hence offer the same technical advantages as the lubricant well which has been described above with reference to Figure 2.
It will be appreciated by those skilled in the art that the invention outlined above provides the considerable advantage over prior axially loaded spherical joint assemblies of reducing the risk of damage to the joint caused by friction between the ball and cup portions.

Claims (15)

1. A ball rod for use in a high-pressure gas compressor, theball rod comprising a rod portion and a substantially spherical ball portion mounted on one end of the rod portion, the ball portion configured to be received in a cup, wherein the ball portion comprises a generally circular lubrication formation provided on a distal portion of the ball portion, and wherein the centres of the lubrication formation and the ball portion lie on a principal longitudinal axis of the rod portion, such that when the ball portion is received within the cup, a lubricant well is formed between the lubrication formation and an inner surface of the cup.
2. A ball rod according to claim 1 wherein the lubrication formation comprises a flat surface.
3. A ball rod according to claim 1 wherein the lubrication formation comprises a concave well.
4. A ball rod according to any of the preceding claims wherein the lubrication formation comprises a radiused edge.
5. A ball rod according to any of the preceding claims wherein the ball portion is constructed from a metallic material.
6. A ball rod according to any of the preceding claims wherein the ball portion is constructed from nitrided steel.
7. A cup for receiving a ball rod according to any of the preceding claims, the cup comprising an inner surface, wherein the inner surface comprises a lubrication formation, such that when the ball rod is received within the cup, a lubricant well is formed between the lubrication formation of the cup and a surface of the ball rod.
8. A cup according to claim 7 wherein the lubrication formation of the cup comprises a cylindrical well.
9. A cup according to claim 7 or claim 8 wherein the cup is constructed from a metallic material.
10. A cup according to any one of claims 7-9 wherein the cup is constructed from nitrided steel.
11. A ball rod substantially as herein before described with reference to the accompanying drawings.
12. A cup substantially as herein before described with reference to the accompanying drawings.
13. An axially loaded spherical joint assembly comprising a ball rod according to any one of claims 1-6 and a cup according to any one of claims 7-10.
14. An axially loaded spherical joint assembly substantially as herein before described with reference to the accompanying drawings.
15. A high-pressure gas compressor comprising an axially loaded spherical assembly according to claim 13 or claim 14.
GB1608080.6A 2016-05-09 2016-05-09 Axially Loaded spherical Joint assembly Active GB2550135B (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
GB1608080.6A GB2550135B (en) 2016-05-09 2016-05-09 Axially Loaded spherical Joint assembly

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
GB1608080.6A GB2550135B (en) 2016-05-09 2016-05-09 Axially Loaded spherical Joint assembly

Publications (3)

Publication Number Publication Date
GB201608080D0 GB201608080D0 (en) 2016-06-22
GB2550135A true GB2550135A (en) 2017-11-15
GB2550135B GB2550135B (en) 2021-08-25

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ID=56297382

Family Applications (1)

Application Number Title Priority Date Filing Date
GB1608080.6A Active GB2550135B (en) 2016-05-09 2016-05-09 Axially Loaded spherical Joint assembly

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Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1283204A (en) * 1968-10-08 1972-07-26 Danfoss As Piston for compressors and the like and method for its manufacture
GB1467531A (en) * 1974-01-28 1977-03-16 Puzey Motion converting machine
DE2723134A1 (en) * 1977-05-23 1978-11-30 Klaue Hermann IC engine of swashplate type - has oil pressure controlled to ensure hydrostatic lubrication of swashplate bearing over entire operating range
JPS5881266A (en) * 1981-11-07 1983-05-16 Toshiba Corp Ball joint piston
JPS58142070A (en) * 1982-02-17 1983-08-23 Toshiba Corp Ball joint piston
JPS5940064A (en) * 1982-08-31 1984-03-05 Toshiba Corp Ball joint for enclosed compressor
JPH03275985A (en) * 1990-03-26 1991-12-06 Sanyo Electric Co Ltd Piston device of compressor
US20050155489A1 (en) * 2003-12-03 2005-07-21 Danfoss Compressors Gmbh Piston arrangement
JP2006322382A (en) * 2005-05-19 2006-11-30 Hitachi Appliances Inc Hermetic compressor
JP2007154806A (en) * 2005-12-07 2007-06-21 Hitachi Appliances Inc Hermetic compressor
JP2014080893A (en) * 2012-10-15 2014-05-08 Hitachi Appliances Inc Hermetic reciprocating compressor and refrigerator using the same

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH05256256A (en) * 1992-03-13 1993-10-05 Hitachi Ltd Ball joint
WO2014011251A2 (en) * 2012-03-26 2014-01-16 Silcotek Corp. Coated article and chemical vapor deposition process
JP2018081266A (en) * 2016-11-18 2018-05-24 パイオニア株式会社 Playback control device
JP6811643B2 (en) * 2017-02-27 2021-01-13 ヤフー株式会社 Golf automatic grouping device, golf automatic grouping method, and program

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1283204A (en) * 1968-10-08 1972-07-26 Danfoss As Piston for compressors and the like and method for its manufacture
GB1467531A (en) * 1974-01-28 1977-03-16 Puzey Motion converting machine
DE2723134A1 (en) * 1977-05-23 1978-11-30 Klaue Hermann IC engine of swashplate type - has oil pressure controlled to ensure hydrostatic lubrication of swashplate bearing over entire operating range
JPS5881266A (en) * 1981-11-07 1983-05-16 Toshiba Corp Ball joint piston
JPS58142070A (en) * 1982-02-17 1983-08-23 Toshiba Corp Ball joint piston
JPS5940064A (en) * 1982-08-31 1984-03-05 Toshiba Corp Ball joint for enclosed compressor
JPH03275985A (en) * 1990-03-26 1991-12-06 Sanyo Electric Co Ltd Piston device of compressor
US20050155489A1 (en) * 2003-12-03 2005-07-21 Danfoss Compressors Gmbh Piston arrangement
JP2006322382A (en) * 2005-05-19 2006-11-30 Hitachi Appliances Inc Hermetic compressor
JP2007154806A (en) * 2005-12-07 2007-06-21 Hitachi Appliances Inc Hermetic compressor
JP2014080893A (en) * 2012-10-15 2014-05-08 Hitachi Appliances Inc Hermetic reciprocating compressor and refrigerator using the same

Also Published As

Publication number Publication date
GB2550135B (en) 2021-08-25
GB201608080D0 (en) 2016-06-22

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