• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    A clocked switchable shut-off valve (2) for capacity control via a temporary shut-off of the suction gas supply is designed as a multi-membered ring valve and actuated directly by means of an electromagnet (12). By means of pressure equalization from the suction gas supply (3) to behind the armature plate (9), the actuating forces for switching over the shut-off valve (2) can be kept small.
    公开号:AT513603A4
    申请号:T50496/2013
    申请日:2013-08-08
    公开日:2014-06-15
    发明作者:Bernhard Dr Spiegl；Andreas Dipl Ing Brandl；Florian Dipl Ing Schacherreiter
    申请人:Hoerbiger Kompressortech Hold；
    IPC主号:
    专利说明:

    828 AT
    Reciprocating compressor with capacity control
    The invention relates to a reciprocating compressor, in particular as refrigeration or Kilmaanla genverdichter, with a capacity control arrangement, which has at least one intake-side arranged and clocked between an open and a closed position switchable shut-off valve for temporary shutdown of the suction gas.
    Compressors with capacity control of the type mentioned are known for example from EP 982497 B1, EP 1515047 B1 or also EP 1279833 B1. Furthermore, JP 63-138490, US 4743168 and other documents also show arrangements for capacity control in particular of multi-cylinder reciprocating compressors, which usually only regulate a part of the cylinders (usually one of several cylinder banks) in the described manner with respect to the delivery rate. In particular, refrigeration and air conditioning systems are operated as a result of constantly changing environmental conditions and required cooling capacities in a wide range of different loads, which for efficient operation requires a simple as possible capacity control system. Disadvantage of all previously known in this context systems is the design of the shut-off valves for controlling the suction gas, which require large valve lifts for correspondingly large flows, which allows only low clock rates.
    Object of the present invention is to improve arrangements of the type mentioned so that the mentioned disadvantages of the previously known arrangements are avoided and that in particular a simple and small-sized operation of quickly clocked switchable shut-off valves with low suction losses is possible.
    This object is achieved according to the present invention in that, in an arrangement of the type mentioned above, the shut-off valve is designed as a multi-membered ring valve and directly actuated by means of a connected to a movable armature plate actuating plunger on the associated valve plate acting electromagnet, one of the Suction gas supply outgoing to the anchor plate leading pressure equalization channel with subsequent pressure compensation surface (pressure compensation piston) is provided. With this ring valve used in reciprocating compressors often as a suction and / or pressure valve very large flow areas with low flow losses can also switch quickly, the advantageous pressure compensation ensures that the required operating forces can be kept as low as possible, which is the direct operation with kleinbauenden Electromagnet (preferably without separate cooling) ermöglichst and keeps the power consumption of the capacity control low.
    However, the greatest advantage of this arrangement is that by using the ring valve with a very small valve lift (for example, 1.5 mm), the required valve cross-section is obtained
    828 AT is enough. Previously known control piston for Zylinderbankabschaltungen cover a single large bore in the valve seat plate. As a result, existing control pistons require very large valve strokes (e.g., 10 mm) to achieve the required flow cross-sections. The large valve lift has a decisive disadvantage. Opening and closing process take a relatively long time. This is on the one hand inefficient because during the opening and closing phase, the flow cross-sections are small, on the other hand it limits the clock rate of the valve. With a small valve lift, the valve can open (close) very quickly, whereby the valve cross-section is immediately released or shut off, the clock frequency can be increased and valve impact speeds remain low (high robustness).
    Cylinder bank shutdowns are used especially with lately actuated operation. However, the clock rate is limited to the top due to the large stroke. The higher the clock rate, the stepless the regulation becomes. Stepped capacity controls have the disadvantage that it is not possible to precisely control the required delivery quantity (= required cooling capacity). This leads to loss of efficiency. Frequency converters solve the problem, but are expensive and can lead to other problems such as vibration. With the solution according to the invention of a fast-clocked cylinder bank deactivation, quasi-stepless regulation is ensured by the highest possible clock rates.
    Basically, it does not matter for the arrangement according to the invention whether the valve plate opens in or against the flow direction of the suction gas - both variants can be realized by appropriate arrangement and design of the shut-off valve including its operation and pressure equalization.
    It is preferably provided that the valve plate is spring-loaded in the opening direction. Furthermore, an electromagnetic actuation could also be provided both in the opening and in the closing direction.
    In a preferred further embodiment of the invention, the pressure equalization channel can run directly through the ring valve together with the actuating plunger and the armature plate, which simplifies the design of the compressor housing and optionally also of the cylinder head. Apart from that, for the sake of simplifying the embodiment of the shut-off valve, the pressure compensation channel can also run in the compressor housing and / or cylinder head.
    The valve seat of the shut-off valve can in a further preferred embodiment of the invention as an additional part in the cylinder head or in the compressor housing mounted, preferably pressed, and optionally - as the valve plate or the entire shut-off valve - be made of plastic. 2 3/8
    828 AT
    The invention is explained in more detail below with reference to the reciprocating compressors shown in the drawing in each case in a detail section in the region of the cylinder head. Fig. 1 shows the clocked for the capacity control switchable shut-off valve in the closed and Fig.2 in the open position and Figures 3 and 4 similar representations of another embodiment.
    The reciprocating compressor shown only schematically in Figures 1 and 2 is preferably used as refrigeration or air conditioning compressor and has an arrangement for capacity control, which arranged at least one suction side before a part of the cylinder 1 and between an open (Fig.2) and a closed Position (Fig.1) clocked switchable shut-off valve 2 for temporary shutdown of the suction gas from the space 3 to these cylinders 1 has. 4 is a here designed as a lamellar valve valve and with a 5 also designed as a multi-valve valve pressure valve, which control the reciprocating movement of the reciprocating piston 6 in the cylinder 1 taking place compression of the pumped from the suction chamber 7 in the pressure chamber 8 gas.
    The shut-off valve 2 is designed as a multi-membered ring valve and actuated directly by means of an actuation plunger 10 connected to a movable armature plate 9 on the associated valve plate 11 electromagnet 12. To reduce the required actuation force out of the suction gas (space 3) outgoing pressure equalization channel 13 is provided through the ring valve 2 together with the actuating plunger 10 and anchor plate 9 to behind the anchor plate 9. The space 18 above the anchor plate 9 is sealed here by means of a sealing ring 14, whereby the pressure prevailing in this space 18 with the shut-off valve 2 substantially corresponds to that in space 3, so when switching off the electromagnet 12, the loading spring 15 and ruling in space 18 Pressure the shut-off valve 2 can very easily reopen (opening against the flow direction, Fig.3 and Fig.4). On the other hand, when switching from the open to the closed position, the pressure building up again in the space 18 acts to support the closing of the shut-off valve (FIGS. 1 and 2).
    Apart from the illustrated embodiment of the pressure equalization channel through the shut-off valve 2, however, corresponding channels could also be provided in the compressor housing 16 and in the cylinder head 17 in order to connect the space 3 with the space 18. Furthermore, apart from the illustrated embodiment, the valve seat could also be provided as a separate part, preferably pressed in the cylinder head. Individual or all parts of the shut-off valve 2 (with the exception, of course, the electromagnet 12) could also be made of plastic.
    With the arrangement shown, a fast-tactile shutdown of individual cylinders or entire cylinder banks for capacity control can be realized, which is also at less than 3 4/8
    828 AT and quickly and with small actuation force to be realized lifting height relatively large flow cross-sections on the check valve 2 ensure low losses and the pressure compensation only relatively low actuation forces for switching the shut-off valve 2 requires.
    In the embodiment according to FIGS. 3 and 4, unlike that according to FIGS. 1 and 2, it is now provided that the valve plate 11 opens against the flow direction of the suction gas (that is, in the representation downward). The electromagnet 12 is therefore above the anchor plate 9, which in turn is connected via the actuating plunger 10 with the valve plate 11, arranged - sealed here via a seal 19 in a bore of the cylinder head 17, via which the anchor plate 9 together with actuating plunger 10 can be installed. The valve plate 11 is also charged here in turn via a loading spring 15 in the opening direction. While the housing-side stop of the anchor plate 9 is formed with open shut-off valve 2 according to Figures 1 and 2 of a disc 20, 3 and 4 a ring 21 is used at the bottom of the anchor plate 9 as shown in FIG.
    The other parts of the embodiment according to FIGS. 3 and 4 are at least functionally similar to those in FIGS. 1 and 2 and are also provided with the same reference numerals.
    In the embodiment according to FIGS. 1 and 2, the pressure compensation surface (lower boundary of space 18) is smaller than the pressure application surface on the shut-off valve 2. As soon as the electromagnet 12 is switched off, the shut-off valve 2 opens in the flow direction (FIG. Due to the larger pressure application surface on the check valve 2 so a net force acts upwards. In contrast, the pressure compensation surface in the embodiment of FIGS. 3 and 4 is greater than the pressure application surface on the shut-off valve 2.
    As soon as the electromagnet 12 is switched off, the shut-off valve 2 thus opens against the flow direction (FIG. 4). Due to the larger pressure application area on the pressure balance piston, a net force acts downwards. 4 5/8
    权利要求:
    Claims (6)
    [1]
    828 AT Claims 1. Reciprocating compressor, in particular as refrigeration or air conditioning compressor, with an arrangement for capacity control, which has at least one on the suction side arranged and clocked between an open and a closed position switchable shut-off valve (2) for temporarily switching off the Saugaszufuhr, characterized in that the shut-off valve (2) is designed as a multi-membered ring valve and is directly actuated by an electromagnet (12) acting on the associated valve plate (11) via an actuating plunger (10) connected to a movable armature plate (9), and one of the suction gas supply (3) outgoing to behind the anchor plate (9) leading pressure equalization channel (13) is provided.
    [2]
    2. Reciprocating compressor according to claim 1, characterized in that the valve plate (11) is spring-loaded in the opening direction.
    [3]
    3. Reciprocating compressor according to claim 1 or 2, characterized in that the pressure equalization channel (13) passes through the annular valve together with confirmation stamp (10) and anchor plate (9).
    [4]
    4. reciprocating compressor according to claim 1 or 2, characterized in that the pressure equalization channel (13) through the compressor housing (16) and / or the cylinder head (17).
    [5]
    5. Reciprocating compressor according to one or more of claims 1 to 4, characterized in that the valve seat of the shut-off valve (2) as an additional part in the cylinder head (17) or in the compressor housing (16) attached, preferably pressed, is.
    [6]
    6. Reciprocating compressor according to claim 5, characterized in that the valve seat, the valve plate (11) or the entire shut-off valve (2) is formed of plastic. 5 6/8
    类似技术:
    公开号 | 公开日 | 专利标题
    AT513603B1|2014-06-15|Reciprocating compressor with capacity control
    DE3909531A1|1990-06-13|Device for saving power in piston compressors, in particular for compressed-air generation in motor vehicles
    DE102008032775A1|2010-01-14|Internal combustion engine with an engine brake device and a valve clearance compensation mechanism
    EP1485585B1|2008-01-30|Device for controlling a gas exchange valve
    DE102007042893A1|2009-03-12|Valve control for reciprocating internal combustion engines
    EP1650434B1|2008-01-23|Multi-stage piston type compressor with reduced power input during idle running
    EP0193640B1|1988-10-26|Seated-valve device
    DE3513461A1|1986-01-02|VALVE UNIT
    EP0767295A1|1997-04-09|Hydraulic valve
    EP1297256B1|2007-07-18|Safety device for an air-conditioning compressor
    EP2511526A1|2012-10-17|Reciprocating piston compressor with transport volume control
    DE102014000469A1|2015-07-16|screw compressors
    DE19841124A1|1999-09-16|Solenoid-operated gas-change valve for piston engine
    EP2456979B1|2016-12-28|Method for controlling delivery quantity, and reciprocating compressor having delivery quantity control
    EP2920499B1|2016-09-21|Valve device and use of such a valve device
    EP0093705A1|1983-11-09|Piston compressor
    EP2456978B1|2016-03-09|Method for controlling delivery quantity and reciprocating compressor having delivery quantity control
    DE2103701A1|1972-08-10|Electro-hydraulic adjustment device
    DE102013209041A1|2014-11-20|Valve device for an internal combustion engine
    DE3546636C2|1996-07-25|Piston compressor
    DE10152503A1|2003-05-08|Device for controlling gas exchange valves
    DE102010041007A1|2012-03-22|Hydraulic piston engine i.e. pump, with variable delivery volume for conveying fuel, has working chamber acting together with control piston, which includes displacement path adjustable by control element
    DE102006036660B4|2015-06-25|Reciprocating internal combustion engine with engine braking by opening the exhaust valves
    DE102010005614B4|2013-11-07|Device for reducing the aerodynamic losses in the intake stroke in the speed and power control of a rotary piston internal combustion engine
    DE1934920C3|1977-06-02|Oscillating piston pump
    同族专利:
    公开号 | 公开日
    CN104343665B|2018-09-04|
    US20150044080A1|2015-02-12|
    AT513603B1|2014-06-15|
    US9567994B2|2017-02-14|
    CN104343665A|2015-02-11|
    DE102014011345A1|2015-02-12|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    DE2302250A1|1973-01-18|1974-08-01|Alexandr Wasiljewitsch Bykow|DEVICE FOR REGULATING THE RECIPROCATING COMPRESSOR PERFORMANCE|
    US4432705A|1978-09-20|1984-02-21|Carrier Corporation|Refrigeration compressor capacity control means and method|
    US4432698A|1980-11-04|1984-02-21|Tokico, Ltd.|Compressor having a starting load reducing apparatus|
    WO2011011221A2|2009-07-20|2011-01-27|Carrier Corporation|Suction cutoff unloader valve for compressor capacity control|WO2016128914A1|2015-02-11|2016-08-18|Dott. Ing. Mario Cozzani S.R.L.|Flow control actuator for reciprocating compressors|US2245053A|1938-09-03|1941-06-10|Westinghouse Electric & Mfg Co|Refrigerating apparatus|
    US2350537A|1941-01-16|1944-06-06|Westinghouse Electric & Mfg Co|Fluid translating apparatus|
    US2730296A|1952-08-09|1956-01-10|Worthington Corp|Unloader mechanism for compressors|
    US3119550A|1961-02-09|1964-01-28|Carrier Corp|Compressor capacity control|
    US4326839A|1979-12-06|1982-04-27|Tecumseh Products Company|Cylinder unloading mechanism for refrigeration compressor|
    US4743168A|1983-03-25|1988-05-10|Carrier Corporation|Variable capacity compressor and method of operating|
    JPS63138490A|1986-11-29|1988-06-10|Konami Kogyo Kk|Vending machine|
    US6206652B1|1998-08-25|2001-03-27|Copeland Corporation|Compressor capacity modulation|
    US6575710B2|2001-07-26|2003-06-10|Copeland Corporation|Compressor with blocked suction capacity modulation|
    AT504695B1|2006-12-22|2008-12-15|Hoerbiger Kompressortech Hold|SUCTION VALVE WITH REMOVABLE GRIPPER|
    CA2749562C|2009-01-27|2014-06-10|Emerson Climate Technologies, Inc.|Unloader system and method for a compressor|
    US20120189467A1|2009-07-23|2012-07-26|Andreas Allenspach|Method for Controlling Delivery Quantity, and Reciprocating Compressor Having Delivery Quantity Control|
    US8840384B2|2009-09-08|2014-09-23|Danfoss Scroll Technologies, Llc|Scroll compressor capacity modulation with solenoid mounted outside a compressor shell|
    EP2683950B1|2011-03-10|2016-07-20|Dresser-Rand Company|Electronic infinite step controller actuator|
    US10378533B2|2011-12-06|2019-08-13|Bitzer Us, Inc.|Control for compressor unloading system|ITMI20130583A1|2013-04-11|2014-10-12|Frascold S P A|COMPRESSOR FOR A REFRIGERATOR SYSTEM AND REFRIGERATING SYSTEM INCLUDING THE COMPRESSOR|
    DE102016009832A1|2016-08-15|2018-02-15|Drägerwerk AG & Co. KGaA|Fluidic actuator, in particular valve, and method of operating a fluidic actuator|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    ATA50496/2013A|AT513603B1|2013-08-08|2013-08-08|Reciprocating compressor with capacity control|ATA50496/2013A| AT513603B1|2013-08-08|2013-08-08|Reciprocating compressor with capacity control|
    DE102014011345.0A| DE102014011345A1|2013-08-08|2014-07-31|Reciprocating compressor with capacity control|
    US14/449,756| US9567994B2|2013-08-08|2014-08-01|Reciprocating compressor having capacity regulation|
    CN201410387762.1A| CN104343665B|2013-08-08|2014-08-08|Piston compressor with power regulation|
    [返回顶部]