Double acting refrigeration compressor

Abstract

A double-acting refrigerant compressor includes a piston freely guided on two cylinder portions arranged opposite to each other and being immobile relative to each other. The piston includes a flow channel extending internally through the piston. Each cylinder portion and the piston include, along the flow channel, respectively at least one back-check valve. The back-check valves are arranged in such a manner that their flow directions are unidirectional.

Claims

1. A double-acting refrigerant compressor comprising a piston freely guided on two cylinder portions of different inner diameters arranged opposite to each other and being immobile relative to each other, said piston guided in said two cylinder portions and driven without a connection to a piston rod, said piston comprising a flow channel extending internally through the piston and each cylinder portion, the flow channel of the piston comprising, respectively, at least one back-check valve, the at least one back-check valve being arranged with a unidirectional flow; and wherein the cylinder portions are spaced from each other in such a manner that a region of the piston is mechanically accessible through a space formed between the spaced cylinder portions from outside the cylinder portions during operation of said double-acting refrigerant compressor; wherein the piston on an end side thereof comprises a low-pressure compression face and on an opposite side comprises a high-pressure compression face which is smaller than the low-pressure compression face; wherein the piston comprises, between the low-pressure compression face and the high-pressure compression face, an auxiliary compression surface which, together with the cylinder portion forming the low-pressure working volume, forms an auxiliary volume to generate a restoring force acting against the driving force of the piston, thereby assisting in controlling the piston, said auxiliary volume disposed axially between an inlet valve plate for a low pressure working volume and said space, and said space disposed axially between said auxiliary volume and an outlet valve plate of a high pressure working volume.

2. The double-acting refrigerant compressor according to claim 1, wherein the piston and the cylinder portions are formed with a rotational symmetry, the at least one back-check valve and the flow channel are arranged on a central longitudinal axis of the piston and the cylinder portions.

3. The double-acting refrigerant compressor according to claim 1, wherein, between the piston and each cylinder portion, a respective compressible working volume is formed adjacent to a back-check valve of a respective cylinder portion and to the at least one back-check valve of the piston.

4. The double-acting refrigerant compressor according to claim 1, wherein the at least one back-check valve of the piston is formed in the high-pressure compression face.

5. The double-acting refrigerant compressor according to claim 1, wherein the piston is driven in a contactless manner by two solenoids operating in opposite senses.

6. The double-acting refrigerant compressor according to claim 1, wherein the piston is guided by a crank drive via an eccentric guide arrangement.

7. The double-acting refrigerant compressor according to claim 1, wherein the piston is provided with an 8-shaped sliding track engaged by a nose of a rotary drive for driving the piston.

8. A double-acting refrigerant compressor for refrigerant recovery comprising: a refrigerant to be recovered; a piston of the double-acting refrigerant compressor having a first piston portion of a first outer diameter and a second piston portion of a second outer diameter; two cylinder portions of said double-acting refrigerant compressor, said two cylinder portions having different cylinder inner diameters including a first cylinder portion having a first cylinder portion inner diameter and a second cylinder portion having a second cylinder portion inner diameter, said two cylinder portions arranged opposite to each other and being immobile relative to each other, said first outer diameter of said first piston portion corresponding to said first cylinder portion inner diameter and said second outer diameter of said second piston portion corresponding to said second cylinder portion, said piston freely guided within said two cylinder portions without a connection to a piston rod; an inlet valve of said double-acting refrigerant compressor, said inlet valve disposed at an inlet plate of the first cylinder portion of said two cylinder portions; an outlet valve of said double-acting refrigerant compressor, said outlet valve disposed at an outlet plate of the second cylinder portion of said two cylinder portions, said second cylinder portion inner diameter being smaller than said first cylinder portion inner diameter; a flow channel of said double-acting refrigerant compressor, said flow channel extending internally through said piston; a flow channel back-check valve of said double-acting refrigerant compressor, said flow channel back-check valve disposed in said flow channel, said flow channel back-check valve to cause a unidirectional flow direction of said refrigerant to be recovered; wherein the cylinder portions are spaced from each other in such a manner that a region of the piston is mechanically accessible through a space formed between the spaced cylinder portions from outside the cylinder portions during operation of said double-acting refrigerant compressor; wherein the piston on an end side thereof comprises a low-pressure compression face and on an opposite side comprises a high-pressure compression face which is smaller than the low-pressure compression face; and wherein the piston comprises, between the low-pressure compression face and the high-pressure compression face, an auxiliary compression surface which, together with the cylinder portion forming the low-pressure working volume, forms an auxiliary volume to generate a restoring force acting against the driving force of the piston, thereby assisting in controlling the piston, said auxiliary volume disposed axially between said inlet valve plate for a low pressure working volume and said space, and said space disposed axially between said auxiliary volume and said outlet valve plate of a high pressure working volume.

9. The double-acting refrigerant compressor of claim 8, wherein a passive pressure compensation takes place between an inlet side and an outlet side of said double-acting refrigerant compressor.

10. The double-acting refrigerant compressor of claim 9, wherein in a refrigerant recycling operation, said double-acting refrigerant compressor removes a refrigerant from a refrigeration system in the absence of a separate bypass line shunting the compressor.

11. A double-acting refrigerant compressor comprising a piston freely guided on two cylinder portions of different inner diameters arranged opposite to each other and being immobile relative to each other, said piston guided in said two cylinder portions and driven without a connection to a piston rod, said piston comprising a flow channel extending internally through the piston and each cylinder portion, the flow channel of the piston comprising, respectively, at least one back-check valve, the at least one back-check valve being arranged with a unidirectional flow; and wherein the cylinder portions are part of a cylinder which is divided into said two cylinder portions being mutually spaced from each other such that the cylinder has an opening in its middle in such a manner that a region of the piston is directly mechanically accessible through a space formed between the spaced cylinder portions from outside the cylinder portions through the opening; wherein the piston on an end side thereof comprises a low-pressure compression face and on an opposite side comprises a high-pressure compression face which is smaller than the low-pressure compression face; and wherein the piston comprises, between the low-pressure compression face and the high-pressure compression face, an auxiliary compression surface which, together with the cylinder portion forming the low-pressure working volume, forms an auxiliary volume to generate a restoring force acting against the driving force of the piston, thereby assisting in controlling the piston, said auxiliary volume disposed axially between an inlet valve plate for a low pressure working volume and said space, and said space disposed axially between said auxiliary volume and an outlet valve plate of a high pressure working volume.

Description

(1) Embodiments of the invention will be described in greater detail hereunder with reference to the Figures. In the Figures, the following is shown:

(2) FIG. 1 shows the first embodiment in a first operating state,

(3) FIG. 2 shows the first embodiment in a second operating state,

(4) FIG. 3 shows a second embodiment in a first operating state,

(5) FIG. 4 shows the second embodiment in a second operating state,

(6) FIG. 5 shows a third embodiment in a first operating state,

(7) FIG. 6 shows the third embodiment in a second operating state,

(8) FIG. 7 shows a fourth embodiment in a first operating state,

(9) FIG. 8 shows the fourth embodiment in a second operating state,

(10) FIG. 9 shows a fifth embodiment,

(11) FIG. 10 shows a sixth embodiment,

(12) FIG. 11 shows a seventh embodiment,

(13) FIG. 12 shows an eighth embodiment, and

(14) FIG. 13 shows a ninth embodiment.

(15) In the refrigerant compressor according to the first embodiment shown in FIGS. 1 and 2, the compressor system comprises the stepped cylinder 1 in which the piston 7 with the central overflow channel 8 is guided in axial direction. The cylinder is terminated by the inlet valve plate 2 and the outlet valve plate 3 in which the inlet valve 10 and respectively the outlet valve 12 are inserted. Overflow channel 8 is terminated by a further valve 11 on the side where the outlet is located.

(16) In this arrangement, the larger-diametered left portion of the stepped cylinder 1 forms the first cylinder portion 41, and the smaller-diametered right-hand portion of the stepped cylinder 1 forms the second cylinder portion 42. Thus, the two cylinder portions 41 and 42 are integrally connected and form the cylinder 1.

(17) The basic function of the double-acting inline free-piston compressor is to be described as follows:

(18) By means of a drive, not yet to be described here, the piston will be brought into a linear oscillatory movement. This can be performed as a resonance oscillation or as a forced oscillation.

(19) Under the functional aspect, the compressor has three characteristic volumes which will influence the work of the system and will determine the force development: the low-pressure working volume 4 the high-pressure working volume 6 the auxiliary volume 5 which assists in controlling the piston (optimally by use of a bypass to the left before valve 10, or to the right from valve 12)

(20) When piston 7 moves to the left, the medium in the low-pressure working volume 4 will be displaced. Since, due to the pressure increase, valve 10 will close, the medium will be forced via overflow channel 8 and overflow valve 11 into the enlarging high-pressure working volume 6. Achieved thereby is a precompression of the medium, said precompression being determined approximately by the ratio between the cylinder cross sections of the low-pressure working volume 4 and the cross section of the high-pressure working volume 6.

(21) As soon as the piston has reached its left-hand turning point, the movement is reversed. The medium will now be displaced from the high-pressure working volume 6 and, via outlet valve 12, will enter the outlet. At the same time, the low-pressure working volume 4 will become larger. The pressure drop in the low-pressure working volume 4 and the increase of the pressure in the high-pressure working volume 6 will cause the overflow valve 11 to be closed. At the same time, the medium will be sucked in from the inlet via inlet valve 10.

(22) As soon as the piston has reached its right-hand turning point, the movement is reversed again and the process is repeated.

(23) In the operational mode for the recycling of refrigerant, the above construction has the advantage that a passive pressure compensation will take place between the inlet and the outlet. In this use, the conventionally required bypass of the state of the art can be omitted. By the construction of the double-acting inline free-piston compressor, the medium can directly flow over through the inlet valve 10, the overflow valve 11 and the outlet valve 12. This can occur as a liquid phase and as a gaseous phase.

(24) After pressure compensation, the steam pressure of the refrigerant, which in the present case can be assumed to be 40 bar, will exist in the low-pressure working volume 4 and in the high-pressure working volume 6. Now, the pressure in the auxiliary volume 5 will take a considerable influence on the force/path behavior of the system. Variant 1: The volume is vented into the ambience. The pressure will thus always be the normal pressure of 1 bar. Variant 2: The volume is gas-tight and is realized with a constant prepressure p.sub.0 as a gas-pressured spring. Variant 3: The volume is connected to the inlet line so that the prepressure is equal to the working pressure in the refrigeration system. Variant 4: The volume is connected to the outlet line so that the prepressure in the auxiliary volume is equal to the working pressure in the recycling container.

(25) A modification of the first embodiment is obtained by opening the cylinder in the middle, so that, as a second embodiment, there is realized a design as depicted in FIGS. 3 and 4 wherein the first cylinder portion 41 is spaced apart from the second cylinder portion 42. Dividing the cylinder into two mutually spaced cylinder portions 41,42 allows for a direct mechanical access to the piston through a space 88 and, thus, also for a drive by use of form-locking engagement.

(26) A further modification results in the third embodiment according to FIGS. 5 and 6 with an inverse compression chamber. The compressor with inverse compression chamber consists of the piston 25 with the overflow channel 8, of the intermediate valve 11 and of the inverse compression chamber 6. The piston 25 is guided in the cylinder 24 which is terminated by the inlet valve plate 2. In the inlet valve plate 2, the inlet valve 10 is mounted. Inlet valve plate 2, cylinder 24 and piston 25 form the low-pressure working volume 4.

(27) Inserted within the inverse compression chamber 6 is the fixed inverse piston 23 with the outlet channel and the outlet valve 12. The cylinder 24 and the inverse piston 23 are tightly connected to each other via a support rack, not illustrated here, and form the stationary system of the compressor.

(28) An advantage of this arrangement is the direct mechanical access to the piston while maintaining the inline flow of the medium, so that, on the one hand, the driving of the piston can also be performed with forced guidance, e.g. by means of a crank drive, and, on the other hand, the medium can flow directly from the inlet through all valves to the outlet.

(29) In the fourth embodiment according to FIGS. 7 and 8, both cylinder portions 41 and 42 are guided as inverse pistons in piston 25.

(30) The fifth embodiment according to FIG. 9 comprises a flat-armature drive for driving the piston. The piston, which itself can be made of a material not relevant for the drive, is mechanically connected to the armature plate 52 made of magnetically soft iron. On both sides, there is arranged a respective pot magnet consisting of the iron core 50 or 54 and of the electric coil 51 or 53. By energizing the coils alternately from both sides, a respective magnetic field is generated between the pot magnet and the armature plate which causes the armature to perform the corresponding movement. For control of the energization, position sensors are required for the piston. In the most simple case, such a sensor can be provided as a slider switch which is operative to switch the energy supply to the other coil when a predetermined end position has been reached.

(31) Other concepts can provide the use of additional electronic elements which will realize the switching not only in dependence on the position but will also include e.g. the speed and the load into the control process. An advantage of this drive resides in that the flat armature has a force/path development which is adaptable to that of the compressor in a favorable manner. Along with a decrease of the air gap between the armature and the magnet, the force will rise in an overproportionate manner, thus allowing particularly the application of the high forces in the piston end positions.

(32) In the sixth embodiment according to FIG. 10, a magnetic spring drive is used for the piston. The operating principle herein consists in a spring-mass oscillator wherein the piston as the mass is excited to perform an oscillating movement. The work to be delivered by the machine has a damping effect and has to be performed as synchronous excitation by the magnet. The principle is very effective for smaller working capacities. To allow for an oscillation to really occur, the kinetic or potential energy stored in the spring-mass system has to be larger than the work to be delivered.

(33) In the seventh embodiment according to FIG. 11, a plunger-type armature is used as a drive for the piston. The coils will generate, in a manner alternating between the two sides, a magnetic flux in the left and in the right region of the plunger armature. The armature will then each time be pulled into the corresponding end position. Also here, it is imperative to achieve an optimized controlling of the coil so as to avoid an unbraked impacting of the armature. Control of the coils is performed in the same manner as in the flat-armature drive.

(34) In the embodiment according to FIG. 12, the piston 7 is driven by a conventional crank drive via an eccentric guide arrangement 61 comprising a shaft 60. Operation of the symmetrically arranged shaft 60 of the rotary drive can be converted into forced oscillation by methods which are also known per se. This approach can be used both for the normal constructional design and for the design with inverse compression chamber. Of advantage herein is the use of normal rotary drives and the forced control of the path.

(35) Alternatively, if a conventional drive is provided, a rotary drive 71 as in FIG. 13, with its rotary axis corresponding to the central longitudinal axis of piston 7, can also serve for engaging, by an interior nose 72, an 8-shaped sliding track 73 arranged on the outer circumferential surface of the piston 7 so that, by rotation of rotary drive 71, piston 7 will be caused to perform an oscillating stroke movement.