US20070041853A1 - Linear compressor, particularly refrigerant compressor - Google Patents
Linear compressor, particularly refrigerant compressor Download PDFInfo
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- US20070041853A1 US20070041853A1 US11/501,271 US50127106A US2007041853A1 US 20070041853 A1 US20070041853 A1 US 20070041853A1 US 50127106 A US50127106 A US 50127106A US 2007041853 A1 US2007041853 A1 US 2007041853A1
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- oil
- piston rod
- piston
- linear compressor
- compressor according
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- 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
Definitions
- the invention concerns a linear compressor, particularly a refrigerant compressor, with a first component group comprising a stator of a linear motor and a cylinder, a second component group comprising a reciprocating piston and an armature of the linear motor as well as a piston rod connecting the armature to the piston, an oil sump in a housing and an oil pump, the second component group being movable in relation to the first component group.
- Such a compressor must currently be supplied with oil.
- the oil has two tasks. Firstly, it lubricates parts, which move in relation to each other. Secondly, it helps sealing a gap between the piston and the cylinder, so that the compression behaviour of the compressor is improved.
- U.S. Pat. No. 6,089,352 shows a linear compressor as mentioned in the introduction.
- the oil pump is fixed on the stator. It has an oblong chamber, whose first end is connected to an oil sump and whose second end is connected to an oil reservoir surrounding the cylinder.
- the stator oscillates with the frequency, with which the piston moves in the cylinder.
- inertia forces which act upon the oil in the chamber during this oscillating movement of the stator, the oil is transported to the oil reservoir.
- it is necessary that the chamber is filled from the beginning. An unfilled chamber cannot work.
- U.S. Pat. No. 5,993,175 shows a further linear compressor, in which the oil pump is located in the stator. It has a pump chamber, in which is located a displacement element that is connected to the stator and the armature via springs. When the armature moves in relative to the stator, the displacement element starts oscillating and sucks oil via a suction pipe from the oil sump into the pump chamber. From here, the oil can reach the piston-cylinder-gap of the compressor via several openings. The displacement element displaces excessive oil from the pump chamber via an outlet opening.
- US 2004/0052658 A1 shows a further linear compressor, in which the stator is connected to an oil pump, which has a pump body that is immersed in the oil sump.
- the pump body has an opening, which extends perpendicularly to the movement direction of the armature.
- the stator oscillates as a reaction to the movement of the armature.
- oil from the oil sump can enter, while the other end of the pump body is connected via a pipe to an oil passage formed in the stator, the oil passage ending in the gap between the piston and the cylinder.
- the cylinder is formed by the inside of the stator and the piston is located in the stator.
- Such oil pumps have a relatively low delivery rate.
- JP 2000 154 778 A2 shows a linear compressor with an oil pump.
- the oil pump has a pump chamber immersing in the oil sump, the pump chamber being formed as a cylinder, in which a piston moves.
- the piston is connected to the armature.
- the piston displaces oil from the pump chamber into an oil reservoir, which again supplies the gap between the piston and the cylinder and a piston rod bearing with oil.
- the oil pump piston sucks in oil through another opening. The path back from the oil reservoir is blocked via a non-return valve.
- Such a pump supplies an increased amount of lubricant.
- it is relatively expensive to manufacture and requires a certain space inside the compressor housing.
- the invention is based on the task of providing a simple design to ensure lubrication for a linear compressor.
- the oil pump has a pump housing that is permanently connected to the piston rod, the pump housing immersing with at least a suction opening into the oil sump, the oil pump supplying oil to the inside of the piston rod.
- the oil pump is located at the end of the piston rod facing away from the piston.
- This embodiment has several advantages. In a manner of speaking, the free end of the piston rod facing away from the piston projects from the stator, so that the pump housing is free to move. Design measures for preventing a collision between the pump housing and other parts of the linear compressor are not necessary.
- the oil is transported through the linear motor, and is thus able to dissipate the heat occurring here. This will heat up the oil and reduce its viscosity, so that it gets highly liquid. This again reduces frictional losses between the piston and the cylinder.
- the piston rod has a channel, which is connected to a piston joint.
- a joint for example, a ball joint.
- the oil from the oil pump is supplied directly into this joint.
- the piston rod is supplied with at least one pressure equalisation opening.
- the channel inside the piston rod will usually not be completely filled with oil. On the contrary, due to gravity the oil will only fill a partial area of the cross-section. Over the oil a gas volume then remains, which is connected to the inner chamber of the compressor housing via the pressure equalisation opening.
- the pressure equalisation opening permits a pressure equalisation, which is particularly advantageous, when leakage gas is pushed backwards from the compression chamber through the lubrication channels inside the piston. An involved pressure build-up could counteract the supply efficiency of the oil pump. This is reliably prevented by the pressure equalisation opening.
- the piston rod has a connecting element to the piston, whose inner diameter tapers.
- a steadily supplied amount will increase the pressure, so that the oil can leave towards the piston at a certain pressure.
- At least one inner diameter reduction is located inside the piston rod. This inner diameter reduction is then some kind of return flow prevention, the return flow prevention managing without movable parts. Nevertheless, within certain limits, it has the same effect as a non-return valve.
- the piston rod has a suction end, whose outer diameter reduces in a direction away from the piston.
- the suction end can also have a slightly conical shape. This reduces the mass of the piston rod at this end.
- fixing the piston rod on the side facing away from the piston will only require smaller surface. This is particularly advantageous, when this end is fixed in a resonance spring arrangement.
- the suction end has a suction channel, which ends inside the piston rod and has a smaller inner diameter than the piston rod, the end of the suction channel being surrounded by a projection pointing in the direction of the piston.
- a relatively large oil volume is permanently available inside the piston rod.
- the cross-section in the suction area is kept small, so that smaller pressures are required to transport the oil from the oil sump to the level of the piston rod.
- the pump housing has a pipe, whose one end is connected with the piston rod, immersing together with the suction opening in the oil sump, the normal to the surface of the suction opening having a component, which is parallel to the movement direction of the first component group.
- the normal to the surface can also be called the axis of the suction opening.
- the normal to the surface is parallel to the movement direction. In this case, the total cross-section of the suction opening is available for the entry of the oil in the movement direction of the piston rod.
- the pump housing has two suction openings in the oil sump, the normals to the surfaces of the suction openings each having a component, which is parallel to the movement direction of the first component group, the components having opposite directions.
- a movement of the piston rod in each direction will give an oil supply, that is, oil will be supplied through the pump housing into the inside of the piston rod in connection with both a suction stroke and a pressure stroke of the piston.
- a blocking element is located between the two suction openings, said blocking element preventing a straight flow of oil from one suction opening to the other. This keeps losses small.
- the blocking element is movable.
- the movement can be initiated by the inertia of the blocking element or by the pressure of the available lubricating oil or by both in common. An additional energy supply or control of the blocking element is thus not required.
- the blocking element exists in the form of a valve element, which is movable between a first valve seat that is allocated to one suction opening and a second valve seat that is allocated to the other suction opening. In this case, the blocking element always blocks the suction opening, through which oil is not presently pressed into the pump housing.
- each suction opening is closed by a spring element, which can be opened by the available oil pressure. Also in this case the passive suction opening is closed, so that oil cannot escape from the pump housing.
- both spring elements are formed by a common spring ring. This simplifies the mounting.
- FIG. 1 is a schematic longitudinal section through a linear compressor
- FIG. 2 is an enlarged view of a piston rod with piston and oil pump
- FIG. 3 is a modified embodiment of an oil pump
- FIG. 4 is a longitudinal section through the oil pump according to FIG. 3 ;
- FIG. 5 is a third embodiment of an oil pump in a section V-V according to FIG. 6 ;
- FIG. 6 is a section VI-VI according to FIG. 5 ;
- FIG. 7 is a fourth embodiment of an oil pump in a perspective view.
- FIG. 8 is a sectional view for explaining an oil pump according to FIG. 7 .
- FIG. 1 shows a linear compressor 1 , which is located in a hermetically closed capsule 2 .
- the linear compressor 1 has a compression section 3 , a drive section 4 and a resonance spring arrangement 5 .
- the unit formed by the compression section 3 , the drive section 4 and the resonance spring arrangement 5 is suspended in the capsule 2 via two plane annular springs 6 , 7 , each formed as a spiral with one winding.
- the annular springs 6 , 7 are fixed on the drive section 4 .
- the compression section 3 has a cylinder 8 , whose one front side is covered by a cylinder head 9 .
- a capsule 10 By means of a capsule 10 , the cylinder 8 and the cylinder body 9 are assembled in the form of a cartridge.
- a suction muffler 11 and a pressure muffler 12 are fixed on the cylinder head 9 .
- the suction muffler 11 is connected with a suction opening 13 and the pressure muffler is connected with a pressure opening 14 in the cylinder head.
- the capsule 10 is inserted in an intermediary ring 15 , which is connected with the drive section 4 .
- the capsule 10 and thus the cylinder 8 can be displaced within certain limits in the axial direction of the cylinder relative to the intermediary ring 15 .
- the capsule 10 is fixed in the intermediary ring 15 , for example by welding, soldering or gluing.
- a piston 16 which borders a compression chamber 17 together with the cylinder 8 and the cylinder head 9 .
- the piston is then expediently moved to its upper dead point (in relation to FIG. 1 : to the right) and the cylinder 8 with the capsule 10 is displaced so that the compression chamber 17 assumes a minimum size.
- the drive section 4 has a linear motor.
- the linear motor has an outer stator 18 with a recess 19 for a winding, not shown in detail, and an inner stator 20 .
- Between the outer stator 18 and the inner stator 20 is an annular gap 21 , in which an armature 22 is movable.
- the armature carries permanent magnets 23 , which are connected with each other by means of two rings 24 , 25 .
- the rings 24 , 25 can, for example, be made of plastic.
- the rings 24 , 25 are connected to inner rings 26 , 27 via arms, not shown in detail, which are guided through slots in the inner stator 20 .
- FIG. 2 shows an enlargement of the piston rod with further details.
- the outer stator 18 and the inner stator 20 are connected with each other via motor covers 29 , 30 , which are tied to each other by means of screw bolts 31 .
- the screw bolts are guided in parallel to the movement direction of the piston rod 28 .
- the piston rod 28 is guided through the motor covers 29 , 30 in a touch-free manner.
- the intermediary ring 15 is connected with the cylinder side motor cover 30 , for example by welding, gluing or soldering.
- the resonance spring arrangement 5 which is located at an end of the drive section 4 opposite the compression section 3 , has a spring pack 32 comprising several plate springs 33 .
- the spring pack 32 is connected to the piston rod 28 in a central area 34 .
- An outer section 35 of the spring pack 32 is connected by means of bolts 36 to a stop housing 37 , which forms a stop for the spring pack 32 .
- the resonance spring arrangement 5 is adapted to the frequency of the current, so that the movable part of the linear compressor 1 , which is formed by the armature 22 , the piston rod 28 , the piston 16 , the oil pump arrangement 38 and the movable part of the resonance spring arrangement 5 , oscillates in resonance.
- the piston rod 28 is connected to an oil pump, which immerses in an oil sump 41 , merely schematically shown in FIG. 2 , which forms in the bottom part of the capsule 2 .
- the oil pump 38 has a pump housing, which is immersed in the oil sump 41 .
- the pump housing 40 is connected to the piston rod 28 by means of a rigid pipe 42 . This means that the pump housing 40 moves synchronously with the piston rod 28 .
- the pump housing 40 has a suction opening 43 , whose normal to the surface is parallel to the movement direction 44 of the piston rod 28 .
- the axis of the suction opening 43 is parallel to the movement direction 44 or the suction opening is perpendicular to the movement direction 44 .
- the channel 45 is connected to a piston joint 46 in the form of a ball joint.
- the piston joint 46 has a ball 47 , which is adopted in a ball socket 48 .
- the contact face between ball 47 and ball socket 48 can be lubricated with oil supplied through the channel 45 .
- the connection between the piston rod 28 and the piston 16 occurs via a connecting element 49 , which tapers conically in the direction towards the piston 16 .
- a connecting element 49 which tapers conically in the direction towards the piston 16 .
- the inner diameter of the channel 45 decreases.
- a pressure balancing opening 50 In the area of the piston 16 is provided a pressure balancing opening 50 .
- the channel 45 inside the piston rod is usually not completely filled with oil, but only in the bottom part. Through the lubricating channels in the piston 16 leakage gas could also be pressed back from the compression chamber into the channel 45 . To prevent this leakage gas from building up a pressure in the channel 45 , which again would counteract the supply effect of the oil pump, the pressure balancing opening 50 is provided for generating a pressure balancing to the inside of the compressor housing.
- the connecting element 49 is attached on the piston rod 28 . It is fixed by frictional forces. If required, it can also be fixed on the piston rod by gluing, welding or soldering. On a whole, it is assumed that also the connecting element 49 is a part of the piston rod 28 .
- the inside of the piston rod has at least one diameter reduction 53 . In the present embodiment, it is formed at the transition between the piston rod and the connecting element 49 . Next to the diameter reduction is formed a recess 54 . In the present case, the recess is realised in the form of an insert 55 , which is inserted into the channel 45 and has an outlet cone 56 on its piston side end.
- the piston rod 28 has a suction end 57 , whose outer diameter reduces in a direction away from the piston 16 .
- the suction end 57 can be screwed onto the piston rod 28 or be glued, welded or soldered onto the piston rod 28 .
- the diameter reduction of the suction end 57 causes that less space is required for fixing the piston rod 28 in the spring pack 32 .
- the suction end 57 has a suction channel 58 , which has a smaller inner diameter than the channel 45 of the piston rod 28 .
- the end of the suction channel 58 into the channel 45 is surrounded by a projection 59 , which points in the direction of the piston 16 .
- a recess 60 forms.
- a return flow prevention device 61 can also be located in the channel 45 , for example in the form of a saw tooth profile, whose piston side end has sides, which are perpendicular or inclined towards the piston 16 , whereas the other sides have a smaller inclination. It is also possible to arrange further “throttling spots” in the channel 45 , which have embodiments similar to those formed by the insert 55 or the projection 59 .
- the oil supply through the unit consisting of piston rod 28 an oil pump arrangement 38 as shown in FIG. 2 can be described as follows:
- the armature 22 reciprocates together with the piston 16 and the oil pump 38 .
- the frequency of this movement corresponds to the frequency of the a.c. supply to the linear motor.
- the recess 60 which surrounds the projection 59 , will prevent it from completely flowing back into the suction channel 58 .
- the inertia of the oil which is pushed in the direction of the cylinder 8 by the projection 59 , will prevent it from flowing back during a return movement of the piston rod 28 .
- it will eventually get through the insert 55 into connecting element 49 . From here, it cannot either completely flow back into the channel 45 , as this is prevented by the outlet cone 56 .
- the oil available in the connecting element 49 can thus only flow on into the ball joint 46 . Additionally, the return flow of the oil can also be prevented or blocked by the return flow prevention device 61 .
- FIGS. 3 and 4 show a modified embodiment of the oil pump arrangement 38 .
- the same elements have the same reference numbers as in FIGS. 1 and 2 .
- the pump housing 40 has two suction openings 43 a , 43 b , which are located opposite each other in the movement direction 44 . Between the two suction openings 43 a , 43 b is located a stop element in the form of a wall 62 , which prevents a straight flow of oil from the suction opening 43 a to the suction opening 43 b or vice versa.
- this oil pump arrangement 38 works exactly as explained in connection with FIG. 2 .
- an oil supply occurs with each movement direction.
- the pump housing 40 is moved to the left, oil is pressed from the oil sump 41 through the suction opening 43 a into the pump housing 40 .
- the pump housing 40 is moved to the right, oil is pressed from the oil sump 41 through the suction opening 43 b into the pump housing 40 .
- the direction details refer to the view in FIG. 4 .
- FIGS. 5 and 6 show a third embodiment of an oil pump housing 40 .
- this oil pump housing 40 has two suction openings 43 a , 43 b located opposite each other.
- the pump housing 40 has an approximately circular inner cross-section.
- a spring plate 63 bent into cylinder shape and covering both suction openings 43 a , 43 b is inserted into this inner cross-section.
- the spring characteristic of this spring plate 63 is relatively soft, so that already small pressures will be sufficient to deform the spring plate 63 so much, that one of the two suction openings 43 a , 43 b is released.
- the oil available in the oil sump 41 will press an arm 63 a of the spring plate 63 into the inside of the pump housing 40 , and the oil can then flow past the arm 63 a into the inside of the pump housing 40 .
- it cannot escape through the oppositely located suction opening 43 b as the incoming oil presses the other arm 63 b firmly against the inner wall of the pump housing 40 and closes the suction opening 43 b .
- the arm 63 b is opened by the available oil and the arm 63 a is kept closed.
- FIGS. 7 and 8 show a fourth embodiment of a pump housing 40 , which again has two suction openings 43 a , 43 b .
- the suction opening 43 a is allocated to a valve seat 64 a and the suction opening 43 b is allocated to a valve seat 64 b .
- a valve element 65 here working as a blocking element, can move between the two valve seats 64 a , 64 b . It therefore comes to rest on the first valve seat 64 a or on the second valve seat 64 b.
- valve element 65 The movement of the valve element 65 is supported by two factors. Firstly, the valve element 65 has a certain inertia, so that a movement of the pump housing 40 to the right (in relation to the view in FIG. 8 ) will bring it to the left valve seat 64 a . This movement is also supported by the oil flowing in through the suction opening 43 b . When, however, the pump housing 40 is moved to the left, the valve element 65 is moved to the right in the pump housing 40 and reaches the valve seat 64 b . Oil from the oil sump 41 can thus only flow in through a suction opening 43 a or 43 b . An escape through the other suction opening 43 b , 43 a is prevented.
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Abstract
The invention concerns a linear compressor (1), particularly a refrigerant compressor, with a first component group comprising a stator (18, 20) of a linear motor (4) and a cylinder (8, 10), a second component group comprising a reciprocating piston (16) and an armature (22) of the linear motor (4) as well as a piston rod (28) connecting the armature (22) to the piston (16), an oil sump in a housing (2) and an oil pump (38), the second component group being movable in relation to the first component group. It is endeavoured to provide a simple design ensuring a lubrication of the linear compressor. For this purpose, the oil pump (38) has a pump housing (40) that is permanently connected to the piston rod (28), the pump housing (40) immersing with at least one suction opening (43; 43 a, 43 b) into the oil sump (41), the oil pump (38) supplying oil to the inside of the piston rod (28).
Description
- Applicant hereby claims foreign priority benefits under U.S.C. § 119 from German Patent Application No. 10 2005 038 784.5 filed on Aug. 17, 2005, the contents of which are incorporated by reference herein. This Application relates to German Patent Applications No. 10 2005 038 783.7 (Attorney Docket No. 6495-0168); No. 10 2005 038 785.3 (Attorney Docket No. 6495-0170); No. 10 2005 038 781.0 (Attorney Docket No. 6495-0172); No. 10 2005 038 780.2 (Attorney Docket No. 6495-0173), filed on the same date herewith.
- The invention concerns a linear compressor, particularly a refrigerant compressor, with a first component group comprising a stator of a linear motor and a cylinder, a second component group comprising a reciprocating piston and an armature of the linear motor as well as a piston rod connecting the armature to the piston, an oil sump in a housing and an oil pump, the second component group being movable in relation to the first component group.
- With such a linear compressor, a corresponding electrical supply of the stator will make the armature reciprocate in the stator. The armature drives the piston in a likewise reciprocating movement. The stator is connected to the cylinder, so that the piston is moved in the cylinder, thus increasing and reducing a compression volume.
- During operation such a compressor must currently be supplied with oil. The oil has two tasks. Firstly, it lubricates parts, which move in relation to each other. Secondly, it helps sealing a gap between the piston and the cylinder, so that the compression behaviour of the compressor is improved.
- U.S. Pat. No. 6,089,352 shows a linear compressor as mentioned in the introduction. The oil pump is fixed on the stator. It has an oblong chamber, whose first end is connected to an oil sump and whose second end is connected to an oil reservoir surrounding the cylinder. During operation, the stator oscillates with the frequency, with which the piston moves in the cylinder. Through inertia forces, which act upon the oil in the chamber during this oscillating movement of the stator, the oil is transported to the oil reservoir. However, it is necessary that the chamber is filled from the beginning. An unfilled chamber cannot work.
- U.S. Pat. No. 5,993,175 shows a further linear compressor, in which the oil pump is located in the stator. It has a pump chamber, in which is located a displacement element that is connected to the stator and the armature via springs. When the armature moves in relative to the stator, the displacement element starts oscillating and sucks oil via a suction pipe from the oil sump into the pump chamber. From here, the oil can reach the piston-cylinder-gap of the compressor via several openings. The displacement element displaces excessive oil from the pump chamber via an outlet opening.
- US 2004/0052658 A1 shows a further linear compressor, in which the stator is connected to an oil pump, which has a pump body that is immersed in the oil sump. The pump body has an opening, which extends perpendicularly to the movement direction of the armature. During operation, the stator oscillates as a reaction to the movement of the armature. Through the opening in the pump body oil from the oil sump can enter, while the other end of the pump body is connected via a pipe to an oil passage formed in the stator, the oil passage ending in the gap between the piston and the cylinder. In this connection, the cylinder is formed by the inside of the stator and the piston is located in the stator.
- Such oil pumps have a relatively low delivery rate.
- JP 2000 154 778 A2 shows a linear compressor with an oil pump. The oil pump has a pump chamber immersing in the oil sump, the pump chamber being formed as a cylinder, in which a piston moves. The piston is connected to the armature. During a stroke of the armature in one direction, the piston displaces oil from the pump chamber into an oil reservoir, which again supplies the gap between the piston and the cylinder and a piston rod bearing with oil. During a return stroke of the armature, the oil pump piston sucks in oil through another opening. The path back from the oil reservoir is blocked via a non-return valve. Such a pump supplies an increased amount of lubricant. However, it is relatively expensive to manufacture and requires a certain space inside the compressor housing.
- The invention is based on the task of providing a simple design to ensure lubrication for a linear compressor.
- With a linear compressor as mentioned in the introduction, this task is solved in that the oil pump has a pump housing that is permanently connected to the piston rod, the pump housing immersing with at least a suction opening into the oil sump, the oil pump supplying oil to the inside of the piston rod.
- The design of such an oil pump is relatively simple and only requires little space. As the pump housing is permanently connected to the piston rod, they reciprocate synchronously. The piston rod has the same stroke as the piston, so that also the pump housing with its suction opening will be moved through the oil sump via a corresponding stroke. Thus, a sufficient amount of oil will reach into the pump housing, the oil being supplied from here to the inside of the piston rod. The piston rod is then used as auxiliary means for transporting the oil to the area of piston and cylinder.
- It is preferred that the oil pump is located at the end of the piston rod facing away from the piston. This embodiment has several advantages. In a manner of speaking, the free end of the piston rod facing away from the piston projects from the stator, so that the pump housing is free to move. Design measures for preventing a collision between the pump housing and other parts of the linear compressor are not necessary. Secondly, the oil is transported through the linear motor, and is thus able to dissipate the heat occurring here. This will heat up the oil and reduce its viscosity, so that it gets highly liquid. This again reduces frictional losses between the piston and the cylinder.
- Preferably, the piston rod has a channel, which is connected to a piston joint. In order to equalise alignment errors, it may be favourable not to locate the piston rigidly on the piston rod, but via a joint, for example, a ball joint. In order to keep the friction small here in spite of possibly occurring small movements, the oil from the oil pump is supplied directly into this joint.
- Preferably, the piston rod is supplied with at least one pressure equalisation opening. The channel inside the piston rod will usually not be completely filled with oil. On the contrary, due to gravity the oil will only fill a partial area of the cross-section. Over the oil a gas volume then remains, which is connected to the inner chamber of the compressor housing via the pressure equalisation opening. Thus, the pressure equalisation opening permits a pressure equalisation, which is particularly advantageous, when leakage gas is pushed backwards from the compression chamber through the lubrication channels inside the piston. An involved pressure build-up could counteract the supply efficiency of the oil pump. This is reliably prevented by the pressure equalisation opening.
- Preferably, the piston rod has a connecting element to the piston, whose inner diameter tapers. Thus, a steadily supplied amount will increase the pressure, so that the oil can leave towards the piston at a certain pressure.
- It is also preferred that at least one inner diameter reduction is located inside the piston rod. This inner diameter reduction is then some kind of return flow prevention, the return flow prevention managing without movable parts. Nevertheless, within certain limits, it has the same effect as a non-return valve.
- This is further improved in that a recess is located adjacent to the inner diameter reduction. A movement of the piston rod in the direction of the cylinder will make the oil dam up in this recess, as basically the oil film is inert and will not on its own follow the movement of the piston rod. When the piston rod is moved in the opposite direction, the inertia of the oil transported through the inner diameter reduction and into the recess will cause it to remain in the position, to which it has been transported, so that subsequent movements of the piston rod over a short period will transport the oil from the pump housing to the position, in which it will evolve its effect.
- Preferably, the piston rod has a suction end, whose outer diameter reduces in a direction away from the piston. At least section-wise, the suction end can also have a slightly conical shape. This reduces the mass of the piston rod at this end. At the same time, fixing the piston rod on the side facing away from the piston will only require smaller surface. This is particularly advantageous, when this end is fixed in a resonance spring arrangement.
- It is preferred that the suction end has a suction channel, which ends inside the piston rod and has a smaller inner diameter than the piston rod, the end of the suction channel being surrounded by a projection pointing in the direction of the piston. This causes that a relatively large oil volume is permanently available inside the piston rod. At the same time, however, the cross-section in the suction area is kept small, so that smaller pressures are required to transport the oil from the oil sump to the level of the piston rod.
- Preferably, the pump housing has a pipe, whose one end is connected with the piston rod, immersing together with the suction opening in the oil sump, the normal to the surface of the suction opening having a component, which is parallel to the movement direction of the first component group. The normal to the surface can also be called the axis of the suction opening. When the normal to the surface or the axis is parallel to the movement direction of the first component group, that is, has a component being parallel to the movement direction of armature, piston rod and piston, the movement of the suction opening will cause oil to be pressed into the suction opening and then, via the pipe, into the inside of the piston rod.
- It is preferred that the normal to the surface is parallel to the movement direction. In this case, the total cross-section of the suction opening is available for the entry of the oil in the movement direction of the piston rod.
- In a preferred embodiment, it is ensured that the pump housing has two suction openings in the oil sump, the normals to the surfaces of the suction openings each having a component, which is parallel to the movement direction of the first component group, the components having opposite directions. In this case, a movement of the piston rod in each direction will give an oil supply, that is, oil will be supplied through the pump housing into the inside of the piston rod in connection with both a suction stroke and a pressure stroke of the piston.
- It is preferred that a blocking element is located between the two suction openings, said blocking element preventing a straight flow of oil from one suction opening to the other. This keeps losses small.
- It is preferred that the blocking element is movable. The movement can be initiated by the inertia of the blocking element or by the pressure of the available lubricating oil or by both in common. An additional energy supply or control of the blocking element is thus not required.
- It is preferred that the blocking element exists in the form of a valve element, which is movable between a first valve seat that is allocated to one suction opening and a second valve seat that is allocated to the other suction opening. In this case, the blocking element always blocks the suction opening, through which oil is not presently pressed into the pump housing.
- In an alternative embodiment it may be provided that each suction opening is closed by a spring element, which can be opened by the available oil pressure. Also in this case the passive suction opening is closed, so that oil cannot escape from the pump housing.
- It is preferred that both spring elements are formed by a common spring ring. This simplifies the mounting.
- In the following, the invention is described on the basis of a preferred embodiment in connection with the drawings, showing:
-
FIG. 1 is a schematic longitudinal section through a linear compressor; -
FIG. 2 is an enlarged view of a piston rod with piston and oil pump; -
FIG. 3 is a modified embodiment of an oil pump; -
FIG. 4 is a longitudinal section through the oil pump according toFIG. 3 ; -
FIG. 5 is a third embodiment of an oil pump in a section V-V according toFIG. 6 ; -
FIG. 6 is a section VI-VI according toFIG. 5 ; -
FIG. 7 is a fourth embodiment of an oil pump in a perspective view; and -
FIG. 8 is a sectional view for explaining an oil pump according toFIG. 7 . -
FIG. 1 shows a linear compressor 1, which is located in a hermeticallyclosed capsule 2. - The linear compressor 1 has a
compression section 3, adrive section 4 and aresonance spring arrangement 5. The unit formed by thecompression section 3, thedrive section 4 and theresonance spring arrangement 5 is suspended in thecapsule 2 via two plane annular springs 6, 7, each formed as a spiral with one winding. Theannular springs 6, 7 are fixed on thedrive section 4. - The
compression section 3 has acylinder 8, whose one front side is covered by a cylinder head 9. By means of acapsule 10, thecylinder 8 and the cylinder body 9 are assembled in the form of a cartridge. Asuction muffler 11 and apressure muffler 12 are fixed on the cylinder head 9. Thesuction muffler 11 is connected with asuction opening 13 and the pressure muffler is connected with a pressure opening 14 in the cylinder head. - The
capsule 10 is inserted in anintermediary ring 15, which is connected with thedrive section 4. During mounting, thecapsule 10 and thus thecylinder 8 can be displaced within certain limits in the axial direction of the cylinder relative to theintermediary ring 15. When, as will be explained below, a predetermined position of the cylinder in relation to thedrive section 4 has been reached, thecapsule 10 is fixed in theintermediary ring 15, for example by welding, soldering or gluing. - In the
cylinder 8 is located apiston 16, which borders acompression chamber 17 together with thecylinder 8 and the cylinder head 9. Before fixing in thecapsule 10 in theintermediary ring 15, the piston is then expediently moved to its upper dead point (in relation toFIG. 1 : to the right) and thecylinder 8 with thecapsule 10 is displaced so that thecompression chamber 17 assumes a minimum size. - The
drive section 4 has a linear motor. The linear motor has anouter stator 18 with arecess 19 for a winding, not shown in detail, and aninner stator 20. Between theouter stator 18 and theinner stator 20 is anannular gap 21, in which anarmature 22 is movable. The armature carriespermanent magnets 23, which are connected with each other by means of tworings rings rings inner rings inner stator 20. - The inner rings 26, 27 are connected with a
piston rod 28, which again is connected with thepiston 16.FIG. 2 shows an enlargement of the piston rod with further details. - The
outer stator 18 and theinner stator 20 are connected with each other via motor covers 29, 30, which are tied to each other by means ofscrew bolts 31. The screw bolts are guided in parallel to the movement direction of thepiston rod 28. Thepiston rod 28 is guided through the motor covers 29, 30 in a touch-free manner. - The
intermediary ring 15 is connected with the cylinderside motor cover 30, for example by welding, gluing or soldering. - The
resonance spring arrangement 5, which is located at an end of thedrive section 4 opposite thecompression section 3, has aspring pack 32 comprising several plate springs 33. Thespring pack 32 is connected to thepiston rod 28 in acentral area 34. Anouter section 35 of thespring pack 32 is connected by means ofbolts 36 to astop housing 37, which forms a stop for thespring pack 32. - When the winding located in the
recess 19 is provided with current, thearmature 22 moves in one direction and takes along thepiston rod 28 in this direction. When the direction of the current is reversed, thearmature 22 with thepiston rod 28 moves in the opposite direction and accordingly moves thepiston 16 in the opposite direction. This will periodically increase and decrease the volume of thecompression chamber 17. Theresonance spring arrangement 5 is adapted to the frequency of the current, so that the movable part of the linear compressor 1, which is formed by thearmature 22, thepiston rod 28, thepiston 16, theoil pump arrangement 38 and the movable part of theresonance spring arrangement 5, oscillates in resonance. - At the end projecting from the
spring pack 32, thepiston rod 28 is connected to an oil pump, which immerses in anoil sump 41, merely schematically shown inFIG. 2 , which forms in the bottom part of thecapsule 2. - The
oil pump 38 has a pump housing, which is immersed in theoil sump 41. Thepump housing 40 is connected to thepiston rod 28 by means of arigid pipe 42. This means that thepump housing 40 moves synchronously with thepiston rod 28. - The
pump housing 40 has asuction opening 43, whose normal to the surface is parallel to the movement direction 44 of thepiston rod 28. In other words, the axis of thesuction opening 43 is parallel to the movement direction 44 or the suction opening is perpendicular to the movement direction 44. When thepiston rod 28 is moved to the left, the oil from theoil sump 41 is pressed through thesuction opening 43 into thepipe 42, the movement of thepiston rod 28 transporting it into the hollow inside 45 of thepiston rod 28. The term “suction opening” is chosen for reasons of clarity here, as the inlet opening of a pump is usually called suction opening. In this case, however, the supply process of theoil pump 38 is less based on suction and more on pressure. - At the piston side end, the
channel 45 is connected to a piston joint 46 in the form of a ball joint. The piston joint 46 has aball 47, which is adopted in a ball socket 48. The contact face betweenball 47 and ball socket 48 can be lubricated with oil supplied through thechannel 45. - The connection between the
piston rod 28 and thepiston 16 occurs via a connectingelement 49, which tapers conically in the direction towards thepiston 16. Thus, the inner diameter of thechannel 45 decreases. In the area of thepiston 16 is provided apressure balancing opening 50. Thechannel 45 inside the piston rod is usually not completely filled with oil, but only in the bottom part. Through the lubricating channels in thepiston 16 leakage gas could also be pressed back from the compression chamber into thechannel 45. To prevent this leakage gas from building up a pressure in thechannel 45, which again would counteract the supply effect of the oil pump, thepressure balancing opening 50 is provided for generating a pressure balancing to the inside of the compressor housing. - The connecting
element 49 is attached on thepiston rod 28. It is fixed by frictional forces. If required, it can also be fixed on the piston rod by gluing, welding or soldering. On a whole, it is assumed that also the connectingelement 49 is a part of thepiston rod 28. - The inside of the piston rod has at least one
diameter reduction 53. In the present embodiment, it is formed at the transition between the piston rod and the connectingelement 49. Next to the diameter reduction is formed arecess 54. In the present case, the recess is realised in the form of aninsert 55, which is inserted into thechannel 45 and has anoutlet cone 56 on its piston side end. - The
piston rod 28 has asuction end 57, whose outer diameter reduces in a direction away from thepiston 16. Thesuction end 57 can be screwed onto thepiston rod 28 or be glued, welded or soldered onto thepiston rod 28. The diameter reduction of thesuction end 57 causes that less space is required for fixing thepiston rod 28 in thespring pack 32. - The
suction end 57 has asuction channel 58, which has a smaller inner diameter than thechannel 45 of thepiston rod 28. The end of thesuction channel 58 into thechannel 45 is surrounded by aprojection 59, which points in the direction of thepiston 16. Radially outside the projection arecess 60 forms. - As shown schematically, a return
flow prevention device 61 can also be located in thechannel 45, for example in the form of a saw tooth profile, whose piston side end has sides, which are perpendicular or inclined towards thepiston 16, whereas the other sides have a smaller inclination. It is also possible to arrange further “throttling spots” in thechannel 45, which have embodiments similar to those formed by theinsert 55 or theprojection 59. - The oil supply through the unit consisting of
piston rod 28 anoil pump arrangement 38 as shown inFIG. 2 can be described as follows: - During operation, the
armature 22 reciprocates together with thepiston 16 and theoil pump 38. The frequency of this movement corresponds to the frequency of the a.c. supply to the linear motor. - When the
piston rod 28 is moved to the left (in relation to the view inFIG. 2 , oil from theoil sump 41 will be pressed into thesuction channel 58 through thesuction opening 43 and thepipe 42. As the stroke length of thesuction opening 43 corresponds to the stroke length of thepiston 16 in thecylinder 8, the supplied amount of oil is sufficient to reach thesuction channel 58. The inertia of the oil causes that at least a share of the oil supplied to thesuction channel 58 remains there. Repeated movement strokes of thepiston rod 28 will thus eventually fill thesuction channel 58, which runs over into thechannel 45. - When the suction channel is filled and the oil runs into the
channel 45, therecess 60, which surrounds theprojection 59, will prevent it from completely flowing back into thesuction channel 58. The inertia of the oil, which is pushed in the direction of thecylinder 8 by theprojection 59, will prevent it from flowing back during a return movement of thepiston rod 28. On the contrary, it will eventually get through theinsert 55 into connectingelement 49. From here, it cannot either completely flow back into thechannel 45, as this is prevented by theoutlet cone 56. The oil available in the connectingelement 49 can thus only flow on into the ball joint 46. Additionally, the return flow of the oil can also be prevented or blocked by the returnflow prevention device 61. - The
FIGS. 3 and 4 show a modified embodiment of theoil pump arrangement 38. The same elements have the same reference numbers as inFIGS. 1 and 2 . - In this case, the
pump housing 40 has twosuction openings 43 a, 43 b, which are located opposite each other in the movement direction 44. Between the twosuction openings 43 a, 43 b is located a stop element in the form of awall 62, which prevents a straight flow of oil from the suction opening 43 a to thesuction opening 43 b or vice versa. - In principle, this
oil pump arrangement 38 works exactly as explained in connection withFIG. 2 . However, here an oil supply occurs with each movement direction. When thepump housing 40 is moved to the left, oil is pressed from theoil sump 41 through the suction opening 43 a into thepump housing 40. When thepump housing 40 is moved to the right, oil is pressed from theoil sump 41 through thesuction opening 43 b into thepump housing 40. Here, the direction details refer to the view inFIG. 4 . - The
FIGS. 5 and 6 show a third embodiment of anoil pump housing 40. Also thisoil pump housing 40 has twosuction openings 43 a, 43 b located opposite each other. Thepump housing 40 has an approximately circular inner cross-section. Aspring plate 63 bent into cylinder shape and covering bothsuction openings 43 a, 43 b is inserted into this inner cross-section. The spring characteristic of thisspring plate 63 is relatively soft, so that already small pressures will be sufficient to deform thespring plate 63 so much, that one of the twosuction openings 43 a, 43 b is released. - When the pump housing is moved to the left (in relation to the view in
FIG. 5 ), the oil available in theoil sump 41 will press an arm 63 a of thespring plate 63 into the inside of thepump housing 40, and the oil can then flow past the arm 63 a into the inside of thepump housing 40. However, it cannot escape through the oppositely located suction opening 43 b, as the incoming oil presses theother arm 63 b firmly against the inner wall of thepump housing 40 and closes thesuction opening 43 b. The same applies for a movement of thepump housing 40 to the right. In this case, thearm 63 b is opened by the available oil and the arm 63 a is kept closed. - The
FIGS. 7 and 8 show a fourth embodiment of apump housing 40, which again has twosuction openings 43 a, 43 b. The suction opening 43 a is allocated to a valve seat 64a and thesuction opening 43 b is allocated to avalve seat 64 b. Avalve element 65, here working as a blocking element, can move between the twovalve seats 64 a, 64 b. It therefore comes to rest on the first valve seat 64 a or on thesecond valve seat 64 b. - The movement of the
valve element 65 is supported by two factors. Firstly, thevalve element 65 has a certain inertia, so that a movement of thepump housing 40 to the right (in relation to the view inFIG. 8 ) will bring it to the left valve seat 64 a. This movement is also supported by the oil flowing in through thesuction opening 43 b. When, however, thepump housing 40 is moved to the left, thevalve element 65 is moved to the right in thepump housing 40 and reaches thevalve seat 64 b. Oil from theoil sump 41 can thus only flow in through a suction opening 43 a or 43 b. An escape through the other suction opening 43 b, 43 a is prevented. - While the present invention has been illustrated and described with respect to a particular embodiment thereof, it should be appreciated by those of ordinary skill in the art that various modifications to this invention may be made without departing from the spirit and scope of the present invention.
Claims (17)
1. A linear compressor, particularly a refrigerant compressor, with a first component group comprising a stator of a linear motor and a cylinder, a second component group comprising a reciprocating piston and an armature of the linear motor as well as a piston rod connecting the armature to the piston, an oil sump in a housing and an oil pump, the second component group being movable in relation to the first component group, wherein the oil pump has a pump housing that is permanently connected to the piston rod, the pump housing immersing with at least one suction opening into the oil sump, the oil pump supplying oil to the inside of the piston rod.
2. The linear compressor according to claim 1 , wherein the oil pump is located at the end of the piston rod facing away from the piston.
3. The linear compressor according to claim 1 , wherein the piston rod has a channel, which is connected to a piston joint.
4. The linear compressor according to claim 1 , wherein the piston rod is supplied with at least one pressure equalisation opening.
5. The linear compressor according to claim 1 , wherein the piston rod has a connecting element to the piston, whose inner diameter tapers.
6. The linear compressor according to claim 1 , wherein at least one inner diameter reduction is located inside the piston rod.
7. The linear compressor according to claim 6 , wherein a recess is located adjacent to the inner diameter reduction.
8. The linear compressor according to claim 1 , wherein the piston rod has a suction end, whose outer diameter reduces in a direction away from the piston.
9. The linear compressor according to claim 8 , wherein the suction end has a suction channel, which ends inside the piston rod and has a smaller inner diameter than the piston rod, the end of the suction channel being surrounded by a projection pointing in the direction of the piston.
10. The linear compressor according to claim 1 , wherein the pump housing has a pipe, whose one end is connected with the piston rod, immersing together with the suction opening in the oil sump, the normal to the surface of the suction opening having a component, which is parallel to the movement direction of the first component group.
11. The linear compressor according to claim 10 , wherein the normal to the surface is parallel to the movement direction.
12. The linear compressor according to claim 10 , wherein the pump housing has two suction openings in the oil sump, the normals to the surfaces of the suction openings each having a component, which is parallel to the movement direction of the first component group, the components having opposite directions.
13. The linear compressor according to claim 12 , wherein a blocking element is located between the two suction openings, said blocking element preventing a straight flow of oil from one suction opening to the other.
14. The linear compressor according to claim 13 , wherein the blocking element is movable.
15. The linear compressor according to claim 14 , wherein the blocking element exists in the form of a valve element, which is movable between a first valve seat that is allocated to one suction opening and a second valve seat that is allocated to the other suction opening.
16. The linear compressor according to claim 13 , wherein each suction opening is closed by a spring element, which can be opened by the available oil pressure.
17. The linear compressor according to claim 16 , wherein both spring elements are formed by a common spring ring.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102005038784.5 | 2005-08-17 | ||
DE102005038784A DE102005038784B3 (en) | 2005-08-17 | 2005-08-17 | Linear compressor, in particular refrigerant compressor |
Related Child Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US12/129,585 Continuation US7778108B2 (en) | 2002-01-11 | 2008-05-29 | Method of and apparatus for processing seismic data |
Publications (1)
Publication Number | Publication Date |
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US20070041853A1 true US20070041853A1 (en) | 2007-02-22 |
Family
ID=37770863
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US11/501,271 Abandoned US20070041853A1 (en) | 2005-08-17 | 2006-08-09 | Linear compressor, particularly refrigerant compressor |
Country Status (3)
Country | Link |
---|---|
US (1) | US20070041853A1 (en) |
CN (1) | CN1952393A (en) |
DE (1) | DE102005038784B3 (en) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20150226203A1 (en) * | 2014-02-10 | 2015-08-13 | General Electric Company | Linear compressor |
WO2020141015A1 (en) * | 2018-12-31 | 2020-07-09 | Gea Bock Gmbh | Compressor |
US11313360B2 (en) * | 2018-08-20 | 2022-04-26 | Lg Electronics Inc. | Linear compressor and method for controlling linear compressor |
Families Citing this family (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN103362783B (en) * | 2013-06-27 | 2015-08-05 | 天津探峰科技有限公司 | A kind of Linearkompressor |
DE102013013252B4 (en) | 2013-08-09 | 2015-04-02 | Technische Universität Dresden | Linear compressor for chillers |
DE102013013251A1 (en) | 2013-08-09 | 2015-02-12 | Technische Universität Dresden | Linear compressor for chillers |
DE102016010567A1 (en) * | 2016-09-02 | 2018-03-08 | Gea Bock Gmbh | compressor |
CN113491179B (en) * | 2021-07-07 | 2022-04-22 | 衢州职业技术学院 | Agricultural machine mobile device |
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US3286933A (en) * | 1964-07-13 | 1966-11-22 | Donald W Barlow | Duplex chemical feeding system |
US5993175A (en) * | 1995-06-23 | 1999-11-30 | Lg Electronics Inc. | Oil supply apparatus for friction portion of linear compressor |
US6089352A (en) * | 1998-05-07 | 2000-07-18 | Lg Electronics, Inc. | Oil supply apparatus for linear compressor |
US20040052658A1 (en) * | 2000-09-06 | 2004-03-18 | Lilie Dietmar Erich Bernhard | Oil pump for a reciprocating hermetic compressor |
US20050123411A1 (en) * | 2003-12-03 | 2005-06-09 | Danfoss Compressors Gmbh | Piston compressor |
US20060216169A1 (en) * | 2004-12-17 | 2006-09-28 | Lg Electronics Inc. | Apparatus for supplying oil of reciprocating compressor |
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JP2000154778A (en) * | 1998-11-17 | 2000-06-06 | Sanyo Electric Co Ltd | Linear compressor |
-
2005
- 2005-08-17 DE DE102005038784A patent/DE102005038784B3/en not_active Expired - Fee Related
-
2006
- 2006-08-09 US US11/501,271 patent/US20070041853A1/en not_active Abandoned
- 2006-08-16 CN CNA2006101495416A patent/CN1952393A/en active Pending
Patent Citations (6)
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US3286933A (en) * | 1964-07-13 | 1966-11-22 | Donald W Barlow | Duplex chemical feeding system |
US5993175A (en) * | 1995-06-23 | 1999-11-30 | Lg Electronics Inc. | Oil supply apparatus for friction portion of linear compressor |
US6089352A (en) * | 1998-05-07 | 2000-07-18 | Lg Electronics, Inc. | Oil supply apparatus for linear compressor |
US20040052658A1 (en) * | 2000-09-06 | 2004-03-18 | Lilie Dietmar Erich Bernhard | Oil pump for a reciprocating hermetic compressor |
US20050123411A1 (en) * | 2003-12-03 | 2005-06-09 | Danfoss Compressors Gmbh | Piston compressor |
US20060216169A1 (en) * | 2004-12-17 | 2006-09-28 | Lg Electronics Inc. | Apparatus for supplying oil of reciprocating compressor |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20150226203A1 (en) * | 2014-02-10 | 2015-08-13 | General Electric Company | Linear compressor |
US9322401B2 (en) * | 2014-02-10 | 2016-04-26 | General Electric Company | Linear compressor |
US11313360B2 (en) * | 2018-08-20 | 2022-04-26 | Lg Electronics Inc. | Linear compressor and method for controlling linear compressor |
WO2020141015A1 (en) * | 2018-12-31 | 2020-07-09 | Gea Bock Gmbh | Compressor |
Also Published As
Publication number | Publication date |
---|---|
DE102005038784B3 (en) | 2007-05-03 |
CN1952393A (en) | 2007-04-25 |
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Legal Events
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AS | Assignment |
Owner name: DANFOSS COMPRESSORS GMBH, GERMANY Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:HANSEN, POUL ERIK;REINWAND, KLAUS;THOMSEN, JAN;AND OTHERS;REEL/FRAME:018707/0809;SIGNING DATES FROM 20061102 TO 20061108 |
|
STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |